CN101506597B

CN101506597B - Refrigeration cycle device and fluid machine used for the same

Info

Publication number: CN101506597B
Application number: CN200780031179.5A
Authority: CN
Inventors: 长谷川宽; 松井大; 尾形雄司; 西胁文俊; 田口英俊; 咲间文顺; 和田贤宣
Original assignee: Matsushita Electric Industrial Co Ltd
Current assignee: Panasonic Holdings Corp
Priority date: 2006-10-25
Filing date: 2007-10-17
Publication date: 2013-01-02
Anticipated expiration: 2027-10-17
Also published as: JP4261620B2; JPWO2008050654A1; CN101506597A; EP2077426A4; WO2008050654A1; US8074471B2; EP2077426A1; JP5178560B2; JP2009092378A; US20100251757A1

Abstract

A refrigeration cycle apparatus (1) includes a refrigerant circuit in which a refrigerant circulates. The refrigerant circuit is formed by connecting in sequence a compressor ((2)) for compressing the refrigerant, a radiator (3) for allowing the refrigerant compressed by compressor ((2)) to radiate heat, a fluid pressure motor (4) as a power recovery means, and an evaporator (5) for allowing the refrigerant discharged by the fluid pressure motor (4) to evaporate. The fluid pressure motor (4) performs a process for drawing the refrigerant and a process for discharging the refrigerant. These processes are performed substantially and continuously.

Description

Freezing cycle device and the fluid machinery that is used for this freezing cycle device

Technical field

The fluid machinery that the present invention relates to a kind of freezing cycle device and be used for this freezing cycle device.

Background technology

Usually, the refrigerant loop of freezing cycle device forms the structure of the evaporimeter of the compressor that connects successively compressed refrigerant, the gas cooler of cooling refrigeration agent, the expansion valve that makes the cold-producing medium expansion and heating and cooling agent.In the freeze cycle of this refrigerant loop, cold-producing medium is from high pressure to inflated with low pressure in expansion valve, and at this moment pressure decreased emits internal energy at the same time.Pressure differential between the low-pressure side of refrigerant loop (vaporizer side) and the high-pressure side (gas cooler side) is larger, and the internal energy of emitting is larger, so the energy efficiency of freeze cycle reduces.

In view of such problem, propose to have all technology that in decompressor, reclaims the internal energy of the cold-producing medium of emitting.For example in JP 2004-44569 communique, the rotating shaft of connection of rotating formula decompressor on the rotating shaft of the motor that is used for the drive compression machine and carry out the technology that energy reclaims.

Figure 26 is the structure chart that carries out the freezing cycle device in the past 501 of energy recovery at the axle 507 of the rotating shaft connection decompressor 504 of the motor 506 that is used for drive compression machine 502.

Freezing cycle device 501 has and connects successively the refrigerant loop that gas cooler 503, decompressor 504, evaporimeter 505 and compressor 502 form as shown in figure 26.Decompressor 504 is to have the rotary type of axle 507 or the decompressor of vortex as rotating shaft.Axle 507 is connected with the motor 506 of drive compression machine 502.The rotating energy of axle 507 (power) passes to the rotating shaft of motor 506.Therefore, the part of the internal energy that cold-producing medium from high pressure to inflated with low pressure and is meanwhile emitted during pressure decreased in decompressor 504 is converted into the rotating energy of axle 507 and passes to motor 506, as the part utilization of the power that is used for drive compression machine 502.Therefore, can realize high energy efficiency according to freezing cycle device 501.

In addition, in JP 57-108555 communique, disclose use do not have intrinsic specific volume (expansion ratio) CD-ROM drive motor and from the technology of refrigerant-recovery energy.Figure 30 is the structure of the disclosed medium-driven motor of expression JP 57-108555 communique and the figure of operating principle.Medium-driven motor 700 has cylinder body 701, at the rotor 702 (piston) of cylinder body 701 interior rotations, will be formed on the blade 705 that operating chamber between cylinder body 701 and the rotor 702 is divided into suction side operating chamber 706a and ejection side operating chamber 706b.Form suction inlets 703 can making cold-producing medium suck suction side operating chamber 706a at cylinder body 701, and form ejiction opening 704 with can be from ejection side operating chamber 706b ejection cold-producing medium.On suction inlet 703 and ejiction opening 704, valve is not set, but the shape of rotor 702 is carried out special design, so that cold-producing medium can be from suction inlet 703 directly to ejiction opening 704 suctions.Particularly, the part of the outer peripheral face of rotor 702 has the radius of curvature identical with the inner peripheral surface of cylinder body 701.

The technology of carrying out power recovery from cold-producing medium is disclosed in the JP 2006-266171 communique.In JP 2006-266171 communique, propose to have the rotating shaft of the rotating shaft of auxiliary compressor of the suction side that is connected at compressor and rotary type decompressor and carry out the technology of power recovery.

Figure 27 is the structure chart that uses the power recovery type freezing cycle device 601 of the compressor with integrated expander 608 of putting down in writing in the JP 2006-266171 communique.As shown in figure 27, freezing cycle device 601 has the refrigerant loop that successively auxiliary connection compressor 602, main compressor 603, gas cooler 604, decompressor 605 and evaporimeter 606 form.

Figure 28 is the profile of compressor with integrated expander 608.Such as Figure 28 and shown in Figure 27, compressor with integrated expander 608 is made of auxiliary compressor 602 and decompressor 605 with the rotating shaft 607 that mutually shares.Therefore, supply with auxiliary compressor 602 by the energy that decompressor 605 reclaims via rotating shaft 607, as the driving force utilization of auxiliary compressor 602.Therefore, according to freezing cycle device shown in Figure 27 601, can realize energy-efficient.

Figure 29 is the profile of decompressor 605.As shown in figure 29, decompressor 605 is oscillating-type decompressors of integrally formed piston 611a and blade 611b.On the blade 611b gumshoe is installed.Be formed with the fine refrigerant path 613 that is communicated with operating chamber 614 on the gumshoe 612.In decompressor 605, blade 611b moves reciprocatingly, and gumshoe 612 carries out oscillating motion.Open and close refrigerant path 613 by the reciprocating motion of this blade 611b and the oscillating motion of gumshoe 612, the suction of cold-producing medium is controlled constantly.

Disclosed decompressor has intrinsic specific volume (sucking the ratio of volume and ejection volume) in JP 2004-44569 communique and the JP 2006-266171 communique.Therefore, in the disclosed decompressor, ejection pressure determines automatically according to the volume of suction pressure and decompressor in JP 2004-44569 communique and JP 2006-266171 communique.But the high pressure of freeze cycle and low pressure are changed at any time by operation condition.Therefore, produce the inconsistent situation of low pressure of ejection pressure (from the pressure of the cold-producing medium of decompressor ejection) with the refrigerant circulation of decompressor.For example in the low situation about forcing down of the ejection pressure ratio freeze cycle of decompressor, produce the overexpansion loss, the problem that the organic efficiency of internal energy of the cold-producing medium of decompressor reduces occurs.

That is, be difficult to reclaim efficiently the cold-producing medium internal energy in the use of the disclosed decompressor of above-mentioned each document.

In addition, Figure 28 and decompressor 605 complex structures shown in Figure 29, cost and productivity existing problems.According to decompressor 605, need to form fine refrigerant path 613 at the gumshoe 612 of oscillating motion.Therefore, if use decompressor 605, then the structure complicated of freezing cycle device causes cost to increase or the productivity reduction easily.

Medium-driven motor 700 shown in Figure 30 owing to there is not an intrinsic volumetric ratio (volumetric ratio is 1), is difficult to be subject to the impact of the pressure state of freeze cycle on the organic efficiency of the energy of cold-producing medium.In addition, since simple in structure, so also be difficult to cause cost and productive problem.But, according to this medium-driven motor 700, shown in the stroke 4 and stroke 5 of Figure 30, the state continuance that only forms an operating chamber 706 in cylinder body 701 is about 90 ° degree to the anglec of rotation of rotor 702, and from stroke 5 as can be known, suction inlet 703 and ejiction opening 704 both by rotor 702 close during the duration longer.Therefore, if medium-driven motor 700 is assembled in the refrigerant loop as power recovery mechanism, then the pulsation of the cold-producing medium of refrigerant loop becomes greatly, becomes the reason that noise and vibration occur.In addition, also produce easily the insufficient lubrication of piston.

Summary of the invention

The present invention researches and develops in view of the above problems, and its purpose is to provide a kind of and can turns round with energy-efficient, and freezing cycle device simple in structure.

That is, among the present invention,

A kind of freezing cycle device, the refrigerant loop that it has refrigerant circulation is characterized in that:

Refrigerant loop has:

The compressor of compressed refrigerant;

Make the radiator by the refrigerant loses heat of compressor compresses;

Basically suck continuously the power recovery mechanism from the ejection stroke of the suction stroke of the cold-producing medium of radiator and the cold-producing medium after this suction of ejection;

Make the evaporimeter by the cold-producing medium evaporation of power recovery mechanism ejection.

In the another side, the invention provides a kind of fluid machinery, it is used for having the freezing cycle device of refrigerant loop, and this refrigerant loop has: the compressor of compressed refrigerant; Make the radiator by the refrigerant loses heat after the compressor compresses; And the evaporimeter that makes the cold-producing medium evaporation,

This fluid machinery is provided with power recovery mechanism, the stroke that this power recovery mechanism sucks from the stroke of the cold-producing medium of radiator basically continuously and the cold-producing medium after will sucking sprays to described vaporizer side.

According to the present invention, can realize turning round with energy-efficient, and freezing cycle device simple in structure.

Description of drawings

Fig. 1 is the structure chart of the freezing cycle device of the first embodiment.

Fig. 2 is the profile of compressor, motor and the fluid pressure motor configuration of expression the first embodiment.

Fig. 3 is that the III-III of Fig. 2 is to view.

Fig. 4 A is that the IV-IV of Fig. 3 is to view.

Fig. 4 B is that the IV-IV of flow direction of expression cold-producing medium is to view.

Fig. 5 is the schematic diagram of movements of the fluid pressure motor of the first embodiment.

Fig. 6 is the Mollier line chart of freeze cycle of the freezing cycle device of the first embodiment.

Fig. 7 is the structure chart that is provided with the freezing cycle device of inner heat exchanger.

Fig. 8 is the curve map of the relation of the specific volume of cold-producing medium of fluid pressure motor of expression the first embodiment and pressure.

Fig. 9 is the structure chart of the freezing cycle device of the second embodiment.

Figure 10 is the profilograph of fluid pressure motor that is provided with the generator of the second embodiment.

Figure 11 is the profilograph of fluid pressure motor that is provided with the generator of variation 1.

Figure 12 is the profile of structure of the fluid pressure motor of expression variation 2.

Figure 13 is the schematic diagram of movements of the fluid pressure motor of variation 2.

Figure 14 is the structure chart of the freezing cycle device of the 3rd embodiment.

Figure 15 is the profile of fluid machinery shown in Figure 14.

Figure 16 is that the D1-D1 of Figure 15 is to view.

Figure 17 is that the D2-D2 of Figure 15 is to view.

Figure 18 is the schematic diagram of movements of fluid pressure motor.

Figure 19 is the schematic diagram of movements of booster.

Figure 20 is that the D3-D3 of Figure 15 is to view.

Figure 21 is the ideograph of the schematic configuration of expression compressor.

Figure 22 is the Mollier line chart of freeze cycle.

Figure 23 is the curve map of the relation of the specific volume of cold-producing medium of expression booster and compressor and pressure.

Figure 24 A is the curve map of relation of the anglec of rotation of the recovery torque of expression fluid pressure motor and axle.

Figure 24 B is the curve map of relation of the anglec of rotation of the expression load torque of booster and axle.

Figure 24 C is the key diagram of the reason of pressure differential counteracting.

Figure 25 is the profile of the booster of variation 1.

Figure 26 is the structure chart of freezing cycle device in the past.

Figure 27 is the structure chart that uses the power recovery type freezing cycle device of compressor with integrated expander in the past shown in Figure 26.

Figure 28 is the profilograph of compressor with integrated expander in the past.

Figure 29 is that the D5-D5 of Figure 28 is to view.

Figure 30 is the schematic diagram of movements of medium-driven motor in the past.

Figure 31 is the structure chart of rotation fluid machinery in the past.

The specific embodiment

Below, with reference to the description of drawings embodiments of the present invention.Wherein, the invention is not restricted to the embodiment of following explanation.In addition, each embodiment can make up again in the scope that does not break away from design of the present invention mutually.

" the first embodiment "

Purpose is on its characteristic of the first embodiment: the freezing cycle device that is applicable to use constrictive medium with the fluid pressure motor that usually only incompressible medium is used as power recovery mechanism, thereby effectively suppress the overexpansion loss, improve the energy efficiency of the running of freezing cycle device.

In addition, in this manual, so-called " fluid pressure motor " refers to: the pressure differential between the pressure (pressure of the cold-producing medium in the pipe arrangement that the ejiction opening of motor connects) of the pressure (pressure of the cold-producing medium of suction) of the cold-producing medium by the suction side and the cold-producing medium of ejection side is rotated, the refrigerant volume of suction is changed, and begin to spray the motor of stroke.At length, the fluid pressure motor refers to not make the motor of refrigerant volume variation before the ejection stroke of the cold-producing medium that sucks begins.In addition, ejection is after stroke begins, and in other words, the inside of fluid pressure motor is with after the ejection path of low pressure is communicated with, the inner pressure relief of fluid pressure motor, cold-producing medium expansion.

Disclosed technology is effective especially for using carbon dioxide etc. to consist of the freezing cycle device of cold-producing medium of supercriticality in the high-pressure side in this specification.Use to consist of in the high-pressure side in the situation of cold-producing medium of supercriticality, the expansion rate of the cold-producing medium that is represented by the ratio of the density of the cold-producing medium of the entrance of the density of the cold-producing medium of the outlet of radiator and evaporimeter is very little.In the energy of effectively emitting when this cold-producing medium expands, the internal energy of emitting based on pressure drop occupies its major part, and the internal energy of emitting based on the increase of specific volume seldom, may lose than overexpansion little under the different situations.Therefore, abandon without hesitation the recovery of the internal energy of emitting based on the increase of specific volume, employing can prevent the structure that the overexpansion loss produces, and is more favourable on energy recovery efficiency than the structure of attempting reclaiming the internal energy of all emitting.

In addition, in the first embodiment, be basically to suck continuously the suction stroke of cold-producing medium and the motor of the ejection stroke of the cold-producing medium of this suction of ejection as the applicable fluid pressure motor of power recovery mechanism.Particularly, constitute there is no the suction path of closing simultaneously cold-producing medium and ejection path during, i.e. at least one open structure in the suction path of cold-producing medium and the ejection path during whole basically.

Therefore, the generation of pressure fluctuation is suppressed.Therefore, the problems such as generation of destabilization, vibration and noise of rotation of breakage, fluid pressure motor that cogging causes of structure member that consist of to suck the freezing cycle devices such as suction line in path are difficult to form.In addition, " there is no the suction path of closing simultaneously cold-producing medium and ejection path during " refers to be included in the concept that moment sucks the situation of path and ejection path closing simultaneously under the degree of the cogging that does not produce the fluid pressure motor.

In addition, as described below the making from least a portion of the cold-producing medium of fluid pressure motor ejection of refrigerant loop becomes gaseous state and consists of.The part of the cold-producing medium of ejection becomes gaseous state, obtains compressibility, thus the Water Hammer that mitigation is caused by the ejection flow velocity that intermittence, the cold-producing medium ejection produced.As a result, the fluid pressure motor is worked more swimmingly, and further absorb vibration and noise.

Below, describe structure and the action effect thereof of the first embodiment in detail with reference to Fig. 1～Fig. 8.

The summary of-freezing cycle device 1-

Fig. 1 is the structure chart of the freezing cycle device 1 of the first embodiment.Freezing cycle device 1 has and connects successively the refrigerant loop that compressor 2, the first heat exchanger 3, fluid pressure motor 4, the second heat exchanger 5 form.Illustrate in the first embodiment and in this refrigerant loop, be filled in the example that consists of the cold-producing medium (being in particular carbon dioxide) of supercriticality the high-pressure side (from the part of compressor 2 via the first heat exchanger 3 arrival fluid pressure motors 4).But among the present invention, it is supercriticality that cold-producing medium is not limited in the high-pressure side, also can be the cold-producing medium (Zhu Ru Fu Liang class etc.) that does not consist of supercriticality in the high-pressure side.

Compressor 2 is driven by motor 6, is HTHP with the refrigerant compression that circulates.The first heat exchanger 3 exchanges by making cold-producing medium and being heated fluid thermal, thereby will form cryogenic high pressure by the refrigerant cools of compressor 2 boil down to HTHPs.Fluid pressure motor 4 sucks the cold-producing medium that is formed cryogenic high pressure by the first heat exchanger 3, goes out to the second heat exchanger 5 side sprays.In the fluid pressure motor 4, the volume of the cold-producing medium of suction is until the ejection stroke begins not variation.The inside of fluid pressure motor 4 is communicated with the ejection path of low pressure, begins when spraying stroke, and the then inner pressure relief of fluid pressure motor 4, the cold-producing mediums in the fluid pressure motor 4 expand and form low pressure.The second heat exchanger 5 is by making cold-producing medium and the fluid thermal exchange of being cooled, thereby will be by the cold-producing medium heating of the low pressure of fluid pressure motor 4 ejections.And suck compressor 2 by the cold-producing medium after 5 heating of the second heat exchanger, also again form HTHP by compressor 2 compressions.Freezing cycle device 1 is by repeatedly carrying out the circulation (freeze cycle) of such cold-producing medium, thereby with the coolings such as extraneous gas (refrigeration) or heating (heating).

The concrete structure of-freezing cycle device 1-

Fig. 2 is the profile (profilograph) of structure of compressor 2, motor 6 and the fluid pressure motor 4 of the embodiment of presentation graphs 1.Fig. 3 is that the III-III of Fig. 2 is to view (drawing in side sectional elevation).Fig. 4 A is that the IV-IV of Fig. 3 is to view (drawing in side sectional elevation).Fig. 5 is the schematic diagram of movements of fluid pressure motor 4, about the state of the per 90 ° of expression fluid pressure motors 4 of the rotation angle θ of axle 51.

As shown in Figure 2, in the present embodiment, compressor 2, motor 6 and fluid pressure motor 4 one are accommodated in the inside of closed container 11, have realized compressionization.

The structure of-motor 6 and compressor 2-

Central configuration at the inner space of closed container 11 11a has motor 6.At length, motor 6 consisting of with respect to stator 6b rotation rotor 6a freely by the stator 6b of the tubular that can not fix rotatably with respect to closed container 11 and the inside of being located at stator 6b.See that on the plane of rotor 6a central authorities are formed with the through hole that connects at direction of principal axis.This through hole insert fixing from the rotor 6a the axle 7 (compressor shaft) of downward-extension.That is, axle 7 rotates by drive motor 6.

Compressor 2 is the compressor of vortex, disposes and be fixed on the top of the inner space 11a of closed container 11.Compressor 2 has fixed turbine 32, revolving wormgear 33, Odum (Oldham) ring 34, parts of bearings 35, muffler 36, suction line 37, bleed pipe 38.

Fixed turbine 32 is mounted to respect to closed container 11 invariant positions.Whirlpool shape cover plate (1ap) 32a of (such as open form shape etc. gradually) is seen on the formation plane below fixed turbine 32.Revolving wormgear 33 and fixed turbine 32 relative configurations are formed with the cover plate 33a that sees swirl shape (such as open form shape gradually etc.) with the plane of cover plate 32a engagement on its surface relative with fixed turbine 32.Between these

cover plates

32a and 33a, divide the operating chamber (discharge chambe) 39 that forms crescent shape.In addition, the contact of the periphery of revolving wormgear 33 also is bearing in the thrust bearing 32b that arranges in downward side-prominent mode, to consist of the periphery of fixed turbine 32.

Chimeric insertion is fixed with the upper end of being located at the axle 7 that extends from rotor 6a and has the eccentric part 7b of the central shaft different from axle 7 on the central portion below revolving wormgear 33.In addition, the downside at revolving wormgear 33 disposes Othemos ring 34.The rotation of these Othemos ring 34 restricting rotation turbines 33, and the effect by this Othemos ring 34, revolving wormgear 33 are accompanied by the rotation of axle 7 and rotatablely move and consist of with the state from the eccentricity of central axis of axle 7.

Be accompanied by the rotation running of revolving wormgear 33, be formed on that operating chamber 39 its volumes between cover plate 32a and the cover plate 33a dwindle and simultaneously outside-in move.Thus, compressed from the cold-producing medium of suction line suction action chambers 39 37.And the cold-producing medium after compressed is via the squit hole 32c of the central portion of being located at fixed turbine 32 and the inner space 36a of muffler 36, and the stream 40 that forms from connecting fixed turbine 32 and parts of bearings 35 is to the inner space 11a ejection of closed container 11.The cold-producing medium of ejection temporarily is trapped among the 11a of inner space.Sneak into the oil (refrigerator oil) of the lubricated usefulness of cold-producing medium between this demurrage by gravity or centrifugal force separate.And the cold-producing medium after oil is separated sprays from bleed pipe 38 to refrigerant loop.

In addition, if compressor 2 has axle 7, and centered by this axle 7, be rotated the compressor of action, then be not limited to the compressor of vortex.For example compressor 2 also can be the compressor of rotary type.

The structure of-fluid pressure motor 4-

As shown in Figure 2, below motor 6, dispose fluid pressure motor 4.In the present embodiment, the example that is made of the fluid pressure motor of rotary type about fluid pressure motor 4 is described." rotary type " comprises rotating piston formula and piston and the integrated swing type that consists of of blade that piston and blade are made of different parts.In addition, fluid pressure motor 4 is not limited to rotary type.Fluid pressure motor 4 for example also can be the fluid pressure motor of vortex.

Fluid pressure motor 4 has the axle 51 as rotating shaft.This axle 51 is connected with axle 7 by joint 13 when assembling, with axle 7 synchronous rotaries.Dispose oil pump 14 in the bottom of axle 51.By this oil pump 14 via being located at oil supplying hole 7a that axle 7 and 51 goes up separately and 51a to supplying with oil lubricated and sealing usefulness in the bearing of compressor 2 and fluid pressure motor 4, the gap etc.

Axle 51 possesses eccentric part 51b, and this eccentric part 51b has with the central shaft different from the central shaft of axle 51.This eccentric part 51b is chimeric with the piston 53 of being located at the tubular (being in particular cylindric) on the periphery of eccentric part 51b.Therefore, piston 53 eccentric rotary motion along with the rotation of axle 51.

Piston 53 its two ends are configured in the cylinder body 52 with inner peripheral surface by the first inaccessible parts 56 and second inaccessible parts 57 obturations of the bearing that doubles as axle 51.Axle 51 connects the center of cylinder body 52.The central shaft of the inner space of cylinder body 52 is consistent with the central shaft of axle 51.Therefore piston 53 is bearing on the axle 51 with the state axle with respect to the eccentricity of central axis of cylinder body 52.And as shown in Figure 3, division is formed with the basically constant operating chamber 60 of volume (total measurement (volume)) between the inner peripheral surface of piston 53 and cylinder body 52.

Be formed with groove 52c with the linear of the internal communication of cylinder body 52 in the top dead centre side of cylinder body 52 (left side among Fig. 3).Dispose the tabular partition member 54 that the slip displacement is disposed freely at this groove 52c.One end of partition member 54 is connected with the spring 55 at the rear that is configured in partition member 54.To the piston 53 direction application of forces, the other end of partition member 54 forms the state on the outer peripheral face that always is pressed over piston 53 by 55 pairs of partition members 54 of this spring.The operating chamber 60 that thus, will be divided formation by piston 53, cylinder body 52, the first inaccessible parts 56 and the second inaccessible parts 57 is divided into the spray action chamber 60b of on high-tension side suction action chamber 60a and low-pressure side.

On the adjacent part of suction action chamber 60a and partition member 54, as shown in Figure 2, opening sucks path 61.This suction path 61 is formed on the first inaccessible parts 56 of the upside that is positioned at cylinder body 52.Sucking path 61 is communicated with suction line 58.Via suck path 61 with cold-producing medium from suction line 58 guiding suction action chamber 60a.On the other hand, the part upper shed adjacent with partition member 54 at spray action chamber 60b has ejection path 62.This ejection path 62 is positioned at the downside of cylinder body 52, is formed on than being formed with on the second inaccessible parts 57 that the first inaccessible parts 56 of sucking path 61 more leave from compressor 2.Ejection path 62 is communicated with bleed pipe 59.Via spraying path 62 with cold-producing medium 59 discharges from spray action chamber 60b to bleed pipe.

As shown in Figure 3, suck path 61 and form roughly fan-shaped with circular-arc extension of the direction of widening from from the part adjacent with partition member 54 of suction action chamber 60a to suction action chamber 60a (Fig. 3 counterclockwise) with respect to the opening 63 (suction inlet 63) of suction action chamber 60a.And only when piston 53 was positioned at the moment of top dead centre, suction inlet 63 was by cylinder body 52 complete atresia.And in the whole period that is positioned at the moment of top dead centre except piston 53, at least a portion of suction inlet 63 becomes the state of opening.Particularly, the end limit 63a that is positioned at the suction inlet 63 in the outside at the radial direction of cylinder body 52 forms circular-arc (radius identical with the outer peripheral face of piston 53 circular-arc) of the outer peripheral face seen on the plane when being positioned at top dead centre along piston 53.

In addition, ejection path 62 forms upper roughly fan-shaped with circular-arc extension of the direction of widening to spray action chamber 60b from the part adjacent with partition member 54 of suction action chamber 60b (Fig. 3 clockwise) with respect to the opening 64 (ejiction opening 64) of spray action chamber 60b.And only when piston 53 was positioned at the moment of top dead centre, ejiction opening 64 was fully by cylinder body 52 lockings.And in the whole period that is positioned at the moment of top dead centre except piston 53, at least a portion of ejiction opening 64 becomes the state of opening.Particularly, the end limit 64a that is positioned at the ejiction opening 64 in the outside at the radial direction of cylinder body 52 forms circular-arc (radius identical with the outer peripheral face of piston 53 circular-arc) of the outer peripheral face of seeing the piston 53 when being positioned at top dead centre on the plane.

Figure 31 represents the structure of rotary type fluid machinery in the past.In this fluid machinery, inlet hole 720 and squit hole 722 are respectively formed at the inner peripheral surface of cylinder body 724.Be positioned at moment of top dead centre at piston 726, inlet hole 720 and squit hole 722 are not closed fully.Therefore, in this moment, fluid can the 722 directly ejections from inlet hole 720 to squit hole by operating chamber 728.The obstacle that the good energy of efficient when this becomes this fluid machinery and uses as power recovery mechanism reclaims.

With respect to this, according to present embodiment, only be positioned at the moment of top dead centre at piston 53, both close suction inlet 63 and ejiction opening 64 fully.Piston 53 slightly rotates from top dead centre, and then operating chamber 60 is divided into suction action chamber 60a and spray action chamber 60b at once, and suction inlet 63 only is communicated with suction action chamber 60a, and ejiction opening 64 only is communicated with spray action chamber 60b.Therefore, can not realize in design that cold-producing medium is from sucking path 61 to the ejection in ejection path 62.Thus, can realize that high efficiency energy reclaims.

In addition, the whole period the moment that is positioned at top dead centre except piston 53, suction inlet 63 is opened, and suck path 61 and be communicated with suction action chamber 60a, and ejiction opening 64 also opens, and sprays path 62 and is communicated with spray action chamber 60b.That is, realized sucking during path 61 and ejection path 62 close simultaneously basically non-existent structure.Therefore, shown in the medium-driven motor 700 in the past as shown in figure 30, be difficult to produce suction inlet 703 and ejiction opening 704 both by rotor 702 sealings during long-time continuing and the problem (mainly being the problem of pulsation) that causes.

In addition, " piston 53 is arranged in the moment of top dead centre " refers to that partition member 54 is pressed into the moment of groove 52c most, and fluid pressure motor 4 becomes the moment of the state shown in the ST1 of Fig. 5.Wherein, " piston 53 is positioned at the moment of top dead centre " is not limited to the moment that piston 53 strictly is positioned at top dead centre, and about can comprising when piston 53 is positioned at top dead centre to a certain degree during.When the anglec of rotation (θ) of the piston 53 when piston 53 is positioned at top dead centre is 0 °, for example the anglec of rotation (θ) of piston 53 be 0 ° ± 5 ° with interior (perhaps 0 ° ± 3 °) during, during suction inlet 63 and ejiction opening 64 both pent structures are also contained in and suck path 61 and ejection path 62 and closed simultaneously basically in the non-existent structure.

In addition, in this first embodiment, the aperture area of ejiction opening 64 is set as larger than the aperture area of suction inlet 63.Relation between the aperture area of the aperture area of suction inlet 63 and ejiction opening 64 without particular limitation of, for example suction inlet 63 can have identical aperture area with ejiction opening 64.

Suck path 61 with respect to the peristome 61c of suction action chamber 60a shown in Fig. 4 A, be formed slopely with respect to the direction of principal axis (above-below direction of Fig. 4 A) of cylinder body 5 the widening that direction is extended of suction action chamber 60a (on high-tension side operating chamber).On the other hand, ejection path 62 is formed slopely with respect to the direction of principal axis of cylinder body 52 the widening that direction is extended of spray action chamber 60b (operating chamber of low-pressure side) with respect to the peristome 62c of spray action chamber 60b.In addition, shown in Fig. 4 A, the bore (internal diameter or sectional area) in ejection path 62 is set greatly than the bore that sucks path 61.

The operating principle of-fluid pressure motor 4-

The operating principle of fluid pressure motor 4 then, is described with reference to Fig. 5.In addition, the figure that in Fig. 5, represents the one of four states of ST1～ST4.ST1 is the anglec of rotation (among θ, Fig. 5 take counterclockwise as just) of piston 53 figure during as 0 °, 360 °, 720 °.ST2 is the figure of the anglec of rotation (θ) of piston 53 when being 90 °, 450 °.ST3 is the figure of the anglec of rotation (θ) of piston 53 when being 180 °, 540 °.ST4 is the figure of the anglec of rotation (θ) of piston 53 when being 270 °, 630 °.

Shown in the ST1 of Fig. 5, when piston 53 is positioned at top dead centre (θ=0 °), suction inlet 63 and ejiction opening 64 are all opened by piston 53, and operating chamber 60 is in not and any isolated state that is communicated with that sucks path 61 and ejection path 62.In these state lower piston 53 rotations, along with θ increases, divide the suction action chamber 60a that forms by outer peripheral face, the first inaccessible parts 56, the second inaccessible parts 57 and the partition member 54 of the inner peripheral surface of cylinder body 52, piston 53 and again form, and its volume there is the trend (ST2～ST4) of increase.Along with the volume of suction action chamber 60a enlarges, the cold-producing medium of the cryogenic high pressure of supplying with from the first heat exchanger 3 sides flows into suction action chamber 60a via sucking path 61.It is 360 ° that this suction stroke proceeds to the anglec of rotation (θ), and namely piston 53 is positioned at top dead centre again.

Again be positioned at moment of top dead centre at piston 53, by piston 53 close suction inlet 63 and ejiction opening 64 both, operating chamber 60 is isolated shown in ST1.Further make afterwards piston 53 rotation, thus ejiction opening 64 open, after this isolated operating chamber 60 is communicated with ejection path 62.Like this, only be positioned at the moment of top dead centre at piston 53, operating chamber 60 is isolated, and suction stroke and ejection stroke carry out basically continuously.The cold-producing medium that sucks does not compress in operating chamber 60 or expands, and from operating chamber 60 ejections.Suck volume and spray volume and basically equate.

By being configured in the function of the compressor 2 in the refrigerant loop, the second heat exchanger 5 sides of fluid pressure motor 4 form low pressure than the first heat exchanger 3 sides.Is communicated with ejection path 62 and makes operating chamber 60 consist of the moment of spray action chamber 60b in above-mentioned isolated operating chamber 60, the cold-producing medium of the cryogenic high pressure that spray action chamber 60b is interior attracted to low-pressure side.So the pressure moment in the 60b of spray action chamber descends, become with the pressure of the low-pressure side of refrigerant loop and equate.Along with the anglec of rotation (θ) change of piston 53 is large, the cold-producing medium in the 60b of spray action chamber sprays to the low-pressure side of refrigerant loop successively.Then, when piston 53 is positioned at top dead centre again (θ=720 °), spray action chamber 60b subdues.With this ejection travel synchronization, again form suction action chamber 60a, carry out ensuing suction stroke.As more than, begin the end when 720 ° of piston 53 rotations of a series of stroke that finishes to the ejection stroke from suction stroke.

This fluid pressure motor 4 by high pressure suction action chamber 60a and the pressure differential capacity between the spray action chamber 60b of low pressure, piston 53 is rotated counterclockwise with the axle 51 that is connected with piston 53.The transmission of torque of axle 51 is given the axle 7 that is connected with axle 51, and conduct is used for the part utilization of the power of compressed refrigerant in compressor 2.

-freeze cycle-

Then, describe the freeze cycle of freezing cycle device 1 in detail with reference to Fig. 6.

Point E shown in Figure 6 is critical point.EL is saturated liquidus.EG is the saturated air line.L _PBe the isobar by critical point (some E).R _TBe the thermoisopleth by critical point (some E).On Mollier line chart shown in Figure 6, saturated air line EG right side and isobar L _PLower zone is gaseous state.Saturated liquidus EL left side and thermoisopleth R _TThe zone of downside be liquid.Isobar L _P, thermoisopleth R _TThe zone of upside is above-critical state.The zone in saturated liquidus EL right side and saturated air line EG left side is gas-liquid two-phase.In addition, the closed loop of the ABCD among Fig. 6 represents the freeze cycle of power recovery type shown in Figure 1.AB in the closed loop of ABCD represents the state variation of the cold-producing medium of compressor 2.BC represents the state variation of the cold-producing medium of the first heat exchanger 3.CD represents the state variation of the cold-producing medium of fluid pressure motor 4.DA represents the state variation of the cold-producing medium of the second heat exchanger 5.

In compressor 2, cold-producing medium is compressed by the above-critical state (some B) to HTHP from the gaseous state (some A) of low-temp low-pressure.Then, cold-producing medium is cooled to the liquid state (some C) of cryogenic high pressure from the above-critical state (some B) of HTHP in the first heat exchanger 3.Afterwards, cold-producing medium liquid state (some C) from cryogenic high pressure in fluid pressure motor 4 expands (pressure drop) to gas-liquid two condition (some D) via saturated solution (some S).In the stroke of this pressure drop (expansion), from a C to a S, cold-producing medium is incompressible liquid state, so the specific volume of cold-producing medium changes hardly.On the other hand, from a S to causing the pressure decreased of following the variation of rapid specific volume, namely follow the pressure decreased of expansion because of the variation from liquid state to gaseous state the D.And cold-producing medium is heated in the second heat exchanger 5, changes to gaseous state (some A) when being accompanied by evaporation from gas-liquid two condition (some D).

The pressure differential of the pressure decreased (SD) of the gas-liquid two condition of fluid pressure motor 4 is compared fully little with the pressure differential of the pressure decreased (CS) of singlet (liquid state).If some C becomes the more some C ' of downside of heat content, then the pressure decreased of gas-liquid two condition changes from SD to S ' D ', and the some C of suction side that such tendency is worked as fluid pressure motor 4 is more more remarkable to low heat content side shifting.

Yet, heat with and supplying hot water with etc. utilize in the situation of high temperature side thermal source of freeze cycle, compare the temperature step-down that is heated medium (for example air or water) that will be heated by the first heat exchanger 3 with the situation of utilizing cooling thermal source such as low temperature side such as grade.Therefore, the tendency of the oriented low heat content side shifting of some C.In addition, shown in Fig. 7 (motor 6 and axle 7 omit), arrange in the situation of inner heat exchanger 18 in the suction side of compressor 2 and the suction side of fluid pressure motor 4, the cold-producing medium that suck compressor 2 carries out heat exchange with the cold-producing medium that will suck fluid pressure motor 4.So as shown in Figure 6, some C is to a C ' movement, some A is to an A ' movement, and freeze cycle forms the state of being determined by the closed loop of A ' B ' C ' D '.Therefore, the tendency that diminishes in the pressure differential of the pressure decreased (SD) of gas-liquid two condition is more remarkable than the tendency that the pressure differential of liquid pressure decreased (CS) diminishes.In addition, this tendency uses carbon dioxide more remarkable than the situation of using Fu Liang or hydrocarbon as the cold-producing medium of freeze cycle.

-effect-

At first, the Ming Dynasty replaces decompressor in the past and uses fluid pressure motor 4 as the resulting action effect of power recovery mechanism with example shown in Figure 8.

Fig. 8 is the specific volume of cold-producing medium of expression fluid pressure motor 4 and the relation of pressure.Among Fig. 8, some C, some D, some S are respectively with the some C of Fig. 6, some D, S is corresponding for point.In addition, Fig. 8 represents that freezing cycle device 1 is used for the result of the computer simulation in the situation of hot-warer supplying machine.The pressure of point C is 9.77Mpa, and temperature is 16.3 ℃.The pressure of point D is 3.96MPa.Point C and point such as are assumed between the D at the heat content.

As shown in Figure 8, in as the pressure drop under the incompressible liquid state (CS), specific volume keeps roughly necessarily and only pressure decreased.In addition, in the pressure drop (SD) of gas-liquid two condition, owing to follow the attitude from the liquid state to the gaseous state to change, so specific volume a larger increase.That is, the pressure drop of liquid (CS) is than the large several times of pressure drop of gas-liquid two condition (SD).

The area of the part that the FCSDHG of Fig. 8 surrounds is equivalent to can be from the theoretical value of the power of the refrigerant-recovery of per unit mass.The theory that is equivalent to the area of the part of being surrounded by this FCSDHG reclaims power W _AllRecovery power W by the pressure drop that surrounded by FCHG _PThe recovery power W that forms with the increase of the specific volume that is surrounded by CSDH _eThe total of (the recovery power of expansion) represents.In model shown in Figure 8, W in fact _pBe W _AllAbout 96%, W _eBe W _AllAbout 4%.Therefore as can be known, based on the recovery power W that expands _eThe shared theoretical power W that reclaims _AllSeldom, its major part recovery power W that is pressure drop _p

The fluid pressure motor 4 that uses as power recovery mechanism in the present embodiment does not make the cold-producing medium of suction expand and makes its ejection, so only can reclaim the theoretical power W that reclaims _AllIn recovery power W _pAmount.With respect to this, use as power recovery mechanism in the situation of decompressor in the past, can reclaim the theoretical power W that reclaims _AllWhole, namely also reclaim to reclaim power W _e

But, as mentioned above, the recovery power W of expansion _eReasonable opinion reclaims power W _AllRatio few, the recovery power W of pressure drop _pAccount for its major part.Therefore, in fact the power that the power that can be reclaimed by fluid pressure motor 4 and decompressor in the past can reclaim do not have that there is a big difference, even can reclaim efficiently power in the situation of use fluid pressure motor 4 yet.Particularly, be in the situation of above-critical state at the high-pressure side of freeze cycle cold-producing medium, utilize heat or the situation of the high temperature side thermal source such as supplying hot water under, the recovery power W of expansion _eThe shared theoretical power W that reclaims _AllConsiderably less.Therefore, even shown in present embodiment, use fluid pressure motor 4 as power recovery mechanism, also can realize the freezing cycle device 1 with the energy-efficient running.

In addition, use as power recovery mechanism in the situation of the decompressor with intrinsic specific volume, might produce the overexpansion loss.With respect to this, shown in present embodiment, do not produce the possibility of overexpansion loss in the situation as power recovery mechanism use fluid pressure motor 4.

If produce the overexpansion loss, then be equivalent to the energy of area of the part of surrounding at DJI shown in dotted lines in Figure 8 as overexpansion loss forfeiture.For example, as shown in Figure 8, if when the specific volume of cold-producing medium expand into as 2.0 times of a C some I, then cold-producing medium is from a D to temporary transient overexpansion the I to the low pressure of pressure than the low-pressure side of freeze cycle.Afterwards, pressure rise is put J to the low pressure of freeze cycle when the beginning of ejection stroke, carries out until the ejection stroke of some G.The loss that the overexpansion of this cold-producing medium causes (overexpansion loss W _Loss), in example for example shown in Figure 8, be equivalent to the theoretical power W that reclaims _AllAbout 3%, and be equivalent to W _AllAbout 4% W _eBe equal to.In addition, W shown in the overexpansion _LossSize according to the operating condition of freezing cycle device 1 and difference also has overexpansion loss W according to operating condition _LossWith the recovery power W based on expansion _eEquate or formation W _eAbove situation.

Like this, also can reclaim W even use in theory _eThe situation of expansion mechanism under, in fact because the overexpansion loss can not stablize and reclaim so big power.With respect to this, use as power recovery mechanism in the situation of fluid pressure motor 4, can reclaim the theoretical power W that reclaims _AllMajor part, and can not produce because of the caused loss of the overexpansion of cold-producing medium W yet _LossTherefore, be not related to the operating condition of freezing cycle device 1, can stablize recovery power.According to circumstances different, can reclaim and be compared to the large power of situation that power recovery mechanism uses decompressor in the past.In other words, use fluid pressure motor 4 as power recovery mechanism, thereby can further improve the average organic efficiency of power.

In addition, fluid pressure motor 4 and decompressor in the past relatively have simple structure, thus use fluid pressure motor 4 as power recovery mechanism, thus can reduce the cost of freezing cycle device 1.In addition, also can reduce the loss that the leakage of loss that the friction because of sliding part and sealing causes and cold-producing medium causes.

In addition, in the present embodiment, do not suck in fact that path 61 and ejection path 62 close simultaneously during, so the ejection of cold-producing medium to the suction that sucks path 61 and cold-producing medium from ejection path 62 is not interrupted, carry out continuously and be actually.In addition, in the fluid pressure motor 4 of present embodiment, the volume of suction action chamber 60a changes with sine wave shape, and only is positioned at top dead centre at piston 53, and the rate of volumetric change of suction action chamber 60a is zero moment, and suction inlet 63 is closed.In other words, the flow velocity of the cold-producing medium that only sucks at suction action chamber 60a of suction inlet 63 is to close moment of zero.In addition, the volume of spray action chamber 60b changes with sine wave shape, and only is positioned at top dead centre at piston 53, and the rate of volumetric change of spray action chamber 60b is zero moment, and ejiction opening 64 is closed.In other words, the flow velocity of the cold-producing medium that only sprays at spray action chamber 60b of ejiction opening 64 is to close moment of zero.Therefore, pressure fluctuation and its water hammer that causes can times establishments.As a result, the breakage of the component parts of freezing cycle device 1, vibration and noise are suppressed.In addition, the cogging of compressor 2 also reduces, and can carry out the running of stable freezing cycle device 1.

In addition, at least a portion from the cold-producing medium of fluid pressure motor 4 ejection is gaseous state.Particularly, spray the cold-producing medium of gas-liquid two conditions from fluid pressure motor 4.At length, with the beginning while of ejection stroke, cold-producing medium decompression, part of refrigerant is changed to gaseous state from liquid state, thereby becomes the gas-liquid two condition.Therefore, even in the present embodiment since ejection moment of cold-producing medium stop, so produce some Water Hammers.But the cold-producing medium of the gaseous state of ejection becomes buffering, and this Water Hammer is relaxed.Therefore, the power of fluid pressure motor 4 can become more smooth.In addition, further absorb vibration and noise.

As Figure 31 is illustrated, form in the structure of suction inlet 720 and ejiction opening 722 at the inner peripheral surface of cylinder body 724, be positioned at moment of top dead centre at piston 726, can not complete atresia suction inlet 720 and ejiction opening 722 both.With respect to this, in the present embodiment, suction inlet 63 is formed on the first inaccessible parts 56, and ejiction opening 64 is formed on the second inaccessible parts 57.Therefore, be positioned at moment of top dead centre at piston 53, both are blocked suction inlet 63 and ejiction opening 64 fully, can establishment 64 the suction from suction inlet 63 to ejiction opening.As a result, efficient power recovery can be realized, the freezing cycle device 1 that turns round with higher efficient can be realized.

In addition, suction inlet 63 also can be formed on the second inaccessible parts 57, and ejiction opening 64 also can be formed on the first inaccessible parts 56.In other words, suck path 61 and also can be formed on the second inaccessible parts 57, ejection path 62 also can be formed on the first inaccessible parts 56.In addition, suction inlet 63 and ejiction opening 64 both also can be formed on the first inaccessible parts 56 or the second inaccessible parts 57.In other words, both also can be formed on the first inaccessible parts 56 or the second inaccessible parts 57 to suck path 61 and ejection path 62.Also can access effect same as described above by such structure.

In addition, piston 53 is positioned at the moment of top dead centre, can close both structures of suction inlet 63 and ejiction opening 64 fully by following realization: the end limit 63a that will be positioned at the radial direction of cylinder body 52 suction inlet 63 in the outside forms the plane and sees circular-arc along the outer peripheral face when piston 53 is positioned at top dead centre, and the end limit 64a of the ejiction opening 64 outside will being positioned at the radial direction of cylinder body 52 forms and sees circular-arc along the outer peripheral face when piston 53 is positioned at top dead centre on the plane.

In the present embodiment, illustrated such as reference Fig. 4 A, peristome 61c is formed slopely with respect to the direction of principal axis of cylinder body 52 along the widening that direction is extended of suction action chamber 60a.In other words, to suck path 61 and the coupling part of suction action chamber 60a be peristome 61c with along with near suction action chamber 60a and away from the inner inclination extension at the first inaccessible parts 56 of the mode of the datum level BH of the central shaft that comprises axle 51 and the center line parallel with the length direction of partition member 54.Thus, shown in Fig. 4 B dotted arrow, the variation of the flow direction of the cold-producing medium in the time of can reducing cold-producing medium suction suction action chamber 60a, the smooth and easy suction suction action chamber 60a of cold-producing medium.Like this, can suppress sharply to change the pressure loss that causes because of the flow direction of cold-producing medium in the suction stroke of cold-producing medium, can improve the efficient of power recovery.

Similarly, peristome 62c also extends and forms with respect to cylinder body 52 tendencies in the direction of the expansion of spray action chamber 60b.In other words, ejection path 62 is peristome 62c with the coupling part of spray action chamber 60b, to comprise mode with the datum level BH of the central shaft of axle 51 and the center line parallel with the length direction of partition member 54 in the oblique extension in the inside of the second inaccessible parts 57 along with more approaching away from spray action chamber 60b.Thus, shown in Fig. 4 B dotted arrow, the variation of the flow direction of the cold-producing medium in the time of can reducing cold-producing medium and spray from spray action chamber 60b, cold-producing medium sprays swimmingly from spray action chamber 60b.Like this, can suppress sharply to change the pressure loss that causes because of the flow direction of cold-producing medium in the ejection stroke of cold-producing medium, can improve the efficient of power recovery.

In addition, suck path 61 and be formed on the first inaccessible parts 56, on the other hand, ejection path 62 is formed on the second inaccessible parts 57 different from the first inaccessible parts 56, thereby prevent from seeing the suction path 61 that relatively approaches and the interference that sprays path 62 on the plane, improve design freedom.This structure is shown in reference Fig. 4 A describes, effective especially when sucking path 61 and ejection path 62 axle with respect to cylinder body 52 and be formed slopely.

In addition, the higher suction path 61 of temperature that is positioned at inner cold-producing medium is formed on the first inaccessible parts 56 near compressor 2, and the lower ejection path 62 of temperature that is positioned at inner cold-producing medium is formed on the second inaccessible parts 57 that leave from compressor 2.Therefore, the heat movement from compressor 2 to fluid pressure motor 4 can be suppressed at irreducible minimum.Therefore, can establishment the first heat exchanger 3 and the second heat exchanger 5 in heat exchange amount reduce, the COP of freeze cycle reduces.

In the present embodiment, the aperture area in the open area ratio suction path 61 in ejection path 62 is large.In other words, the aperture area of ejiction opening 64 is set as larger than the aperture area of suction inlet 63.The cold-producing medium of ejection has larger specific volume than the cold-producing medium that sucks, so the pressure loss the when ratio of the pressure loss when spraying cold-producing medium sucks cold-producing medium is large.If form the structure that increases ejiction opening 64, the pressure loss when then spraying cold-producing medium can effectively be reduced, and can make up the pressure loss that reduces cold-producing medium.Therefore, can further improve the efficient of power recovery.

The viewpoint of the pressure loss from establishment more from the fluid pressure motor during 4 ejection cold-producing medium also can arrange a plurality of ejiction openings 64.In addition, from same insight, as reference Fig. 4 A was illustrated, it greatly also was effective making the bore in the relative aperture suction path 61 in ejection path 62.

In addition, in the present embodiment, adopt the fluid pressure motor 4 of the rotary type of 1 cylinder body that is not provided with the such sucker mechanism of valve system.Thus, compare and to reclaim power with simple structure with the situation of the rotary type expansion mechanism that uses 1 cylinder body with scroll expansion machine or multistage rotary type decompressor, sucker mechanism in the past etc.Therefore, can realize cheaply simultaneously, and can reduce the friction loss that causes and to improve mechanical efficiency by reducing sliding part because of machinery.In addition, in addition, the mobile use of the parts of rotary compressor is easy, also can expect further cost.

" the second embodiment "

In the first above-mentioned embodiment, illustrated that the axle 51 of fluid pressure motor 4 is connected with the axle 7 of motor 6, directly supply with the example of compressor 2 by the energy of fluid pressure motor 4 recovery.But, the invention is not restricted to this, for example also the energy that is reclaimed by fluid pressure motor 4 temporarily can be converted to electric energy.In the second embodiment, such structure example has been described.In addition, in the explanation in the present embodiment, Fig. 3 and the common reference of above-mentioned the first embodiment.In addition, the Reference numeral that structural element uses and above-mentioned the first embodiment is common with substantially the same function describes, and it illustrates omission.Wherein, as detailed below, in the present embodiment, cold-producing medium consists of to the suction direction-agile of fluid pressure motor 4, so suction line 58 as the first tube connector 58, bleed pipe 59 as the second tube connector 59, suck path 61 as the first path 61, ejection path 62 is as 62 explanations of the second path.

Fig. 9 is the structure chart of freezing cycle device 8 of the power recovery formula of the second embodiment.Figure 10 is the profilograph of fluid pressure motor 4 with generator 15 of the second embodiment.

As mentioned above, the freezing cycle device in the present embodiment 8 is different from the freezing cycle device 1 of above-mentioned the first embodiment aspect unconnected at the axle 7 of the axle 51 of fluid pressure motor 4 and motor 6.In the present embodiment, as shown in Figure 9 and Figure 10, the axle 51 of fluid pressure motor 4 is different from generator 15.

Particularly, as shown in figure 10, generator 15 is realized compressionization in fluid pressure motor 4 is accommodated in closed container 16.Generator 15 have can not rotate and can not displacement stator 15b cylindraceous on the ground mount pad closed container 16.In the inside of stator 15b, the rotor 15a cylindraceous with the little a little external diameter of internal diameter than stator 15b can dispose with respect to stator 15b rotationally.In the inside of rotor 15a, can not rotate and can not insert up or down the fixedly axle 51 of fluid pressure motor 4.Then, drive fluid pressure motor 4 is accompanied by the rotation of axle 51, and rotor 15a rotates relatively with respect to stator 15b, forms thus the structure of generating.In addition, this generator 15 can both generate electricity in the situation that axle 51 turns clockwise and situation about being rotated counterclockwise.

Diagram not in Fig. 9 and Figure 10, but generator 15 and supply lines electrical connection to the motor 6 of drive compression machine 2 are supplied with motor 6 by the electric power of generator 15 generatings, use as the part of the power of drive compression machine 2.

As shown in Figure 9, in the present embodiment, in refrigerant loop, be provided with the cross valve 9 as the switching mechanism of the flow direction that can switch compressed cold-producing medium.Therefore, can change the flow direction by compressor 2 compression and the cold-producing medium extruded.

Particularly, connect the suction inlet (suction line 37) of compressors 2 and ejiction opening (bleed pipe 38) and the first heat exchanger 3, the second heat exchanger 5 at cross valve 9.And, by operation cross valve 9, thereby the ejiction opening that can switch compressor 2 is connected with the first heat exchanger 3, on the other hand, the first connection status (connection status among Fig. 9 shown in the solid line) that the suction inlet of compressor 2 is connected with the second heat exchanger 5 is connected with the second heat exchanger 5 with ejiction opening with compressor 2, on the other hand, the second connection status (connection status shown in dotted lines in Figure 9) that the suction inlet of compressor 2 is connected with the first heat exchanger 3.

In the second connection status, supply with the second heat exchanger 5 by compressor 2 compression and the cold-producing medium that forms HTHP.In this case, the second heat exchanger 5 plays the function as gas cooler (radiator).Cold-producing medium is cooled in the second heat exchanger 5, and forms cryogenic high pressure.The cold-producing medium of formation cryogenic high pressure flows into operating chamber 60 from the second tube connector 59 of fluid pressure motor 4 via the second path 62.Cold-producing medium in the operating chamber 60 goes out to the first heat exchanger 3 side sprays from the first tube connector 58 via the first path 61.And, in the first heat exchanger 3, be heated and the cold-producing medium that gasifies is brought into play compressor 2 again.Therefore, under this second connection status, rotate with making axle 51 on the first reverse connection directions direction.

In the first connection status, with above-mentioned the first embodiment similarly, the first heat exchanger 3 plays the function as gas cooler (radiator), the second heat exchanger 5 plays the function as evaporimeter.On the other hand, opposite with above-mentioned the first embodiment in the second connection status, the first heat exchanger 3 plays the function as evaporimeter, and the second heat exchanger 5 plays the function as gas cooler (radiator).Therefore, according to the freezing cycle device 8 of this second embodiment, such as the cooling (refrigeration) that can carry out refrigerating and heating combined equipment etc. and heating (heating) both.

As more than, if switch connection status from the first connection status to the second connection status, then the direction of rotation of the axle 7 of compressor 2 does not change, but the direction of rotation of the axle 51 of fluid pressure motor 4 changes, the direction of rotation of axle 7 and axle 51 is opposite.Therefore, shown in the first embodiment, be connected with the axle 7 of compressor 2 at the axle 51 of fluid pressure motor 4, always make axle 7 and axle 51 interlocks and in the structure of rotating, can not switch the first connection status and the second connection status.Therefore, in the first embodiment, only by importing a cross valve 9, can not change the flow direction by the cold-producing medium of compressor 2 compressions.

With respect to this, shown in present embodiment, in the situation that axle 7 and axle 51 independent rotations consist of, also can make axle 7 and axle 51 mutual counter-rotatings.Namely, when by formation cross valve 9 being set, the structure that axle 51 is connected with generator 15 and generates electricity, and can reclaim power, and can realize cooling off (refrigeration) and heating (heating) both refrigerating and heating combined equipments (refrigeration-heating air-conditioner etc.).

In addition, in the decompressor with natural scale ratio, the cold-producing medium that need to flow in the direction that the volume that makes operating chamber enlarges can not be at the mobile cold-producing medium of contrary direction.Therefore, only by expansion valve is converted to decompressor, can not realize changeable as the present embodiment a plurality of connection status.With respect to this, in the fluid pressure motor because the flow direction of cold-producing medium determines, thus only the fluid pressure motor is used for replacing expansion valve as mentioned above, just can realize easily can high efficiency recovery internal energy refrigeration-heating air-conditioner etc.In addition, the cross valve that also is useful on the circulating direction that switches cold-producing medium only has one with regard to enough advantages.

More than, as the first and second embodiments, the example that the fluid pressure motor with the rotary type of a cylinder body uses as power recovery mechanism is described.But the switching mechanism that switches the first state and the second state is not limited to cross valve, such as also using bridge circuit etc.

In addition, the fluid pressure motor is not limited to this structure, for example also can be the fluid pressure motor of the rotary type of multi-cylinder body.In addition, also can be the fluid pressure motor scroll fluid pressure motor for example of the mode beyond the rotary type.

In following variation 1, the example that uses the rotary type fluid pressure motor of 2 cylinder bodies as the variation of the second embodiment is described.In addition, in variation 2, can substitute the fluid pressure motor of vortex of the fluid pressure motor of the illustrated rotary type of the first and second embodiments.In addition, in the explanation of following variation 1, Fig. 9 and the common reference of above-mentioned the second embodiment.In addition, the structural element with substantially the same function is to describe with the common Reference numeral of above-mentioned the first and second embodiments, and it illustrates omission.

" variation 1 "

Figure 11 is the profilograph of fluid pressure motor 4a with generator 15 of variation 1.Fluid pressure motor 4a is 2 cylinder body types with two

cylinder body

52a and 52b.

In the present embodiment 1, be provided with two eccentric part 51b1 and 51b2 at axle 51.The upper state with off-centre of eccentric part 51b1 is equipped with piston 53a.Piston 53a is accommodated among the cylinder body 52a by the inaccessible two ends of inaccessible parts 56a and 57a.Form operating chamber 60c by piston 53a, inaccessible parts 56a, inaccessible parts 57a and cylinder body 52a division.Operating chamber 60c is divided into two spaces (suction action chamber and spray action chamber) by spring 55a to the partition member 54a of the piston 53a direction application of force.

On the other hand, the state with off-centre is equipped with piston 53b on eccentric part 51b2.Piston 53b is accommodated among the cylinder body 52b by the inaccessible two ends of inaccessible parts 56b (common with inaccessible parts 57a) and 57b.Form operating chamber 60d by piston 53b,

inaccessible parts

56b, 57b and cylinder body 52b division.Operating chamber 60d by by spring 55b on piston 53b direction the partition member 54b of the application of force be divided into two spaces (suction action chamber and spray action chamber).

Be formed with the first path 61 at inaccessible parts 56a.The other end that this first path 61 connects the first tube connector 58 that at one end is connected with the first heat exchanger 3 connects.In addition, first connect 61 be divided into by above-mentioned partition member 54a two operating chamber 60c a side and again the above-mentioned partition member 54b side that is divided into two operating chamber 60d be communicated with.

Be formed with the second path 62a at inaccessible parts 57a.The other end that this second path 62a connects the second tube connector 59a that at one end is connected with the second heat exchanger 5 connects.In addition, the second path 62a is communicated with the opposing party who is divided into two operating chamber 60c by above-mentioned partition member 54a.On the other hand, be formed with the second path 62b at inaccessible parts 57b.This second path 62b is connected with the second tube connector 59b.In addition, the second path 62b is communicated with the opposing party who is divided into two operating chamber 60d by above-mentioned partition member 54b.In addition, the second tube connector 59b is connected on the second heat exchanger 5 with the second tube connector 59a.

On the first connection status of reference Fig. 9 explanation, shown in solid arrow among Figure 11, supply with two operating chamber 60cs and 60d from the first tube connector 58 via the first path 61 from the cold-producing medium of the first heat exchanger 3.And the cold-producing medium in the operating chamber 60c goes out to the second heat exchanger 5 side sprays from the second tube connector 59a via the second path 62a.In addition, the cold-producing medium in the operating chamber 60d goes out to the second heat exchanger 5 side sprays from the second tube connector 59b via the second path 62b.Under the second connection status, at the mobile cold-producing medium of the direction shown in the dotted arrow.

Like this, the fluid pressure motor 4a of variation 1 be divided into by above-mentioned partition member 54a two operating chamber 60c a side and be divided into by above-mentioned partition member 54b two operating chamber 60d a side both be communicated with first common paths 61 and consist of.Wherein, also can be communicated with separately the first different paths with 60d and consist of at operating chamber 60c.That is, also can the first special-purpose path be set in each operating chamber.

In this variation 1, a plurality of

piston

53a, 53b uniformly-spaced are positioned on the direction of rotation of axle 51 each top dead centre and dispose.Particularly, two

piston

53a, 53b uniformly-spaced are positioned at relatively configuration on the direction of rotation of axle 51 with each top dead centre.Therefore, the phase place of the phase place of piston 53a and piston 53b staggered for 1/2 cycle mutually.

According to said structure, by piston 53a and the 53b cogging of can cancelling out each other.Therefore, the rotation of fluid pressure motor 4a is more stable, can absorb vibration and noise.Particularly, in the fluid pressure motor, because refrigerant pressure sharply changed from suction pressure cutter ejection pressure when the ejection stroke began, so compare with the decompressor with expansion stroke, it is large that the vibration of ejection and noise become easily, therefore, shown in variation 1, form 2 cylinder bodies and the effect that plays is significant.

In addition, cylinder body also can arrange more than 3.In this case, preferred disposition becomes top dead centre separately uniformly-spaced to be positioned on the direction of rotation of axle 51.The 120 ° of configurations of preferably mutually staggering particularly, are set in the situation of three cylinder bodies.

" variation 2 "

In this variation 2, the structure example of the fluid pressure motor of vortex is described with reference to Figure 12 and Figure 13.In addition, in the explanation of present embodiment 2, the structural element that basically has identical function uses above-mentioned the first and second embodiments and variation 1 shared Reference numeral to describe, and it illustrates omission.

The structure of the fluid pressure motor 4b of-vortex-

As shown in figure 12, fluid pressure motor 4b has revolving wormgear 71, fixed turbine 72, Othemos ring 34a, parts of bearings 35a, suction line 73, bleed pipe 74.

Fixed turbine 72 can not displacement and is not installed with respect to closed container 16 revolvably.On fixed turbine 72, be formed with the gradually roll film 72a of open form shape.On the other hand, revolving wormgear 71 and fixed turbine 72 relative configurations form the roll film 71a with the gradually open form shape of roll film 72a engagement on the surface relative with this fixed turbine 72.Divide formation operating chamber 75 by these

roll films

72a and 71a.

Be fixedly installed the eccentric part from axle 51 different central shafts of having on the bottom of axle 51 in the chimeric insertion of center upper portion section of revolving wormgear 71.In addition, the upside at revolving wormgear 71 disposes Othemos ring 34a.The rotation of this Othemos ring 34a restricting rotation turbine 71, the function by this Othemos ring 34a is so that revolving wormgear 71 is followed the rotation of axle 51 and rotatablely moved with the state with respect to the eccentricity of central axis of axle 51 consists of.

Be formed with on the central portion of plane that switching is opened in operating chamber 75 freely seeing and be connected to the suction path 72b that is connected with suction line 73 outside the closed container 16 at fixed turbine 72.Suck path 72b with in the cold-producing medium suction action chamber 75 via this.

The operating principle of the fluid pressure motor 4b of-turbine type-

The operating principle of fluid pressure motor 4b then, is described with reference to Figure 13.In addition, the figure that in Figure 13, represents the one of four states of S1～S4.The anglec of rotation of axle 51 represents by φ, take the state shown in the S1 as φ=0 ° describe.

Under the state shown in the S1, the inner peripheral surface of the top of roll film 72a contact roll film 71a, the inner peripheral surface of the top contact roll film 72a of roll film 71a.Form and the suction action chamber 75a that sucks path 72b and be communicated with by fixed turbine 72 chord rotating turbine 71.

Along with revolving wormgear 71 rotation, it is large that rotationangleφ becomes, and the contact P1 of revolving wormgear 71 and fixed turbine 72 and P2 are mobile laterally, sucks cold-producing medium from sucking path 72b, and the volume of suction action chamber 75a enlarges (with reference to suction stroke: S2～S4) simultaneously.

Then when the state that again returns shown in the S1, namely suck to form during φ=360 ° and finish.At length, contact P1 is positioned at the terminal of the roll film 72a of fixed turbine 72, and contact P2 is positioned at the top of the roll film 71a of revolving wormgear 71 on the other hand.And shown in S1, revolving wormgear 71 and fixed turbine 72 also contact on the contact P3 of contact P1 and P2 inboard and P4.Thus, suction action chamber 75a and suction path 72b blocking, two isolated operating chamber 75b of formation crescent shape.

Rotationangleφ surpasses 360 °, and then contact P1 and P2 eliminate.That is, the terminal of the roll film 71a of revolving wormgear 71 is left from the roll film 72a of fixed turbine 72, and on the other hand, the terminal of the roll film 72a of fixed turbine 72 is left from the roll film 71a of revolving wormgear 71.Thus, two isolated operating chamber 75b are communicated with bleed pipe 74 separately, form spray action chamber 75.And along with anglec of rotation Φ continues to increase from 360 °, the volume reducing of spray action chamber 75c is along with the cold-producing medium in the 75c of spray action chamber sprays (ejection stroke) from bleed pipe 74.

As described above, only the moment in φ=0 °, revolving wormgear 71 contacts at these four points of contact P1～P4 with fixed turbine 72, and operating chamber is isolated.In addition, revolving wormgear 71 only contacts these 2 of contact P1 and contact P2 with fixed turbine 72, and suction action chamber 75a always is communicated with suction path 72b, and spray action chamber 75b always is communicated with bleed pipe 74 on the other hand.By such structure, realize the fluid pressure motor 4b of vortex.

Even in the situation that the fluid pressure motor 4b of the vortex of explanation uses as the power recovery mechanism of freezing cycle device in this variation 2, similarly can realize efficient power recovery with the situation of the fluid pressure motor of the rotary type of explanation in the above-described embodiment.Like this, can realize freezing cycle device with the running of high efficiency.

In addition, the fluid pressure motor 4b of vortex of explanation in the present embodiment 2, with the fluid pressure motor 4 of the rotary type of above-mentioned first and second embodiment explanation similarly, the direction of flow of refrigerant is not determined.That is, the fluid pressure motor 4b of vortex also can replace suction inlet and ejiction opening turns round.Therefore, also can replace the fluid pressure motor 4 of the second embodiment, and use the fluid pressure motor 4b of present embodiment 2.

" the 3rd embodiment "

Present embodiment, the booster that configuration is made of the fluid pressure motor between evaporimeter and compressor, the power drive that this booster is reclaimed by the power recovery mechanism that is made of the fluid pressure motor.Like this, by at freezing cycle device configuration power recovery mechanism and the power-actuated booster by being reclaimed by this power recovery mechanism, thereby can improve the efficiency of freezing cycle device.In addition, by consisting of booster and power recovery mechanism by the fluid pressure motor with the simpler structure of compressor and decompressor, thus can be simply and the structure of stroke freezing cycle device at an easy rate.The basic structure of the fluid pressure motor of the fluid pressure motor that uses in the present embodiment and the explanation of the embodiment of front is common.

Below, with reference to Figure 14～Figure 15 freezing cycle device in the present embodiment is described.

The summary of-freezing cycle device 101-

Figure 14 is the structure chart of the freezing cycle device 101 of embodiment.Freezing cycle device 101 is provided with the refrigerant loop 109 that comprises compressor 103, gas cooler 104, power recovery mechanism 105, evaporimeter 106, booster 102.The cold-producing medium that is filled in the refrigerant loop 109 for example is carbon dioxide or fluorohydrocarbon.In situation about using as carbon dioxide at the cold-producing medium of the high-pressure side of freeze cycle formation supercriticality, as previously mentioned, be to bring into play the peculiar outstanding effect of the present invention.

Compressor 103 has compressing mechanism 103a (compressor main body), the motor 108 that is connected with compressing mechanism 103a, takes in the housing 160 of compressing mechanism 103a and motor 108.Compressing mechanism 103a is driven by motor 108.Compressing mechanism 103a will be HTHP at the refrigerant compression of refrigerant loop 109 interior circulations.Compressing mechanism 103a for example can be scroll compressor, also can be rotary compressor.

Gas cooler (radiator) 104 is connected with compressor 103.Gas cooler 104 makes the refrigerant loses heat by compressor 103 compressions.In other words, gas cooler 104 will be by the refrigerant cools of compressor 103 compressions.Cold-producing medium displacement cryogenic high pressure by gas cooler 104 coolings.

Power recovery mechanism 105 is connected with gas cooler 104.Power recovery mechanism 105 is made of the fluid pressure motor.Particularly, power recovery mechanism 105 sucks the stroke from the stroke of the cold-producing medium of gas cooler 104 and the cold-producing medium ejection that will suck basically continuously.That is, power recovery mechanism 105 sucks the cold-producing medium that is become cryogenic high pressure by gas cooler 104, basically change in volume does not occur and goes out to evaporimeter 106 side sprays.At this, make gas cooler 104 sides become higher high pressure by compressor 103 across power recovery mechanism 105, evaporimeter 106 sides become lower low pressure.Therefore, the cold-producing medium that is absorbed by power recovering mechanism 105 expands when driven force recovering mechanism 105 sprays, and forms low pressure.

Evaporimeter 106 is connected with power recovery mechanism 105.Evaporimeter 106 is cold-producing medium heating and the evaporation of ultromotivity recovering mechanism 105 in the future.

Booster 102 is configured between evaporimeter 106 and the compressor 103.Booster 1 02 is connected with power recovery mechanism 105 by axle 12.The power drive of booster 102 by being reclaimed by power recovery mechanism 105.Booster 102 similarly is made of the fluid pressure motor with power recovery mechanism 105.Booster 102 sucks the stroke of cold-producing medium of flash-pot 106 and the stroke that the cold-producing medium that will suck goes out to compressor 103 side sprays basically continuously.Booster 102 sucks the cold-producing medium of flash-pot 106, there is no change in volume occurs and to go out to compressor 103 side sprays.Thereby the cold-producing medium that comes flash-pot 106 is prepared from booster 102 ejections and boosts.The cold-producing medium that preparation is boosted is by compressor 103 compressions and again become HTHP.

The concrete structure of-freezing cycle device 101-

-fluid machinery 110-

As shown in figure 15, power recovery mechanism 105 and booster 102 consist of a fluid machinery 110.Fluid machinery 110 has and is frozen the closed container 111 that machine oil is full of.Power recovery mechanism 105 and booster 102 are configured in this closed container 111.Thus, realize the compression of freezing cycle device 101.

(structure of power recovery mechanism 105)

Power recovery mechanism 105 is configured in the bottom of closed container 111.In addition, in the present embodiment, the example that is made of the fluid pressure motor of rotary type about power recovery mechanism 105 has been described.Wherein, power recovery mechanism 105 can by the fluid pressure motor beyond the rotary type for example the fluid pressure motor of vortex shown in Figure 12 consist of.

Power recovery mechanism 105 has the first hermetic unit 115 and the second hermetic unit 113.The first inaccessible parts 115 and the second inaccessible parts 113 are oppositely arranged.Between the first inaccessible parts 115 and the second inaccessible parts 113, dispose the first cylinder body 22.The inner space that the first cylinder body 22 has general cylindrical shape.The inner space of this first cylinder body 22 is by the first inaccessible parts 115 and the second inaccessible parts 113 obturations.

Axle 12 on the direction of principal axis of the first cylinder body 22 in the 22 interior perforations of the first cylinder body.Axle 12 is configured on the central shaft of the first cylinder body 22.Axle 12 is by the above-mentioned second inaccessible parts 113 and the described later the 3rd inaccessible parts 114 supportings.Be formed on the oil supplying hole 12a that is connected by axle 12 on the direction of principal axis on the axle 12.Via this oil supplying hole 12a the refrigerator oils in the closed container 111 are supplied with in the bearing of booster 102 and power recovery mechanism 105 or the gap etc.

First piston 21 is configured in the inner peripheral surface of the first cylinder body 22 and the first inaccessible parts 115 and the second inaccessible parts 113 and divides in the inner space of the general cylindrical shape that forms.First piston 21 is with the state embedded axle 12 with respect to the eccentricity of central axis of axle 12.Particularly, axle 12 possesses the eccentric part 12b that has different central shafts from the central shaft of axle 12.Embed the first piston 21 of barrel shape at this eccentric part 12b.Therefore, first piston 21 is with respect to the eccentricity of central axis of the first cylinder body 22.Therefore, first piston 21 is followed the rotation of axle 12 and the eccentric rotary motion.

Inner peripheral surface by this first piston 21 and the first cylinder body 22 and the first inaccessible parts 115 and the second inaccessible parts 113 form the first operating chamber 23 (simultaneously with reference to Figure 16) in the 22 interior divisions of the first cylinder body.Even the first operating chamber 23 first pistons 21 are with axle 12 rotations, its volume is in fact also constant.

As shown in figure 16, be formed with groove 22a at the linear of the first operating chamber 23 openings at the first cylinder body 22.Insert sliding freely the first tabular partition member 24 on this lines groove 22a.Dispose force application mechanism 25 between the bottom of the first partition member 24 and lines groove 22a.Pressured towards the outer peripheral face of first piston 21 by these force application mechanism 25, the first partition members 24.Thus, the first operating chamber 23 is divided into two spaces.Particularly, the first operating chamber 23 is divided into the spray action chamber 23b of on high-tension side suction action chamber 23a and low-pressure side.

In addition, force application mechanism 25 for example can be made of spring.Particularly, force application mechanism 25 can be compression disc spring.

In addition, force application mechanism 25 also can be the gas spring of conduct etc.Namely, also can be the first partition member 24 when when the direction of the volume-diminished of the backside space of the first partition member 24 is slided, pressure setting in its backside space be higher than the pressure of the first operating chamber 23, the depended on pressure that acts on to first piston 21 directions with respect to the first partition member 24 by this pressure differential.For example, also can with the backside space of the first partition member 24 as confined space, when the volume of backside space reduces by retreating of the first partition member 24, apply reaction force to the first partition member 24.Certainly, force application mechanism 25 also can be made of multiple springs such as compression disc spring and gas springs.In addition, the pressure of the first operating chamber 23 is average pressures of the pressure of the pressure of so-called suction action chamber 23a and spray action chamber 23b.Backside space refers to be formed on the space between the bottom of the rear end of the first partition member 24 and lines groove 22a.

On the part adjacent with the first partition member 24 of suction action chamber 23a, as shown in figure 16, offer and suck path 27.As shown in figure 15, this suction path 27 is formed on the second inaccessible parts 113 of the downside that is positioned at the first cylinder body 22.As shown in figure 15, sucking path 27 is communicated with suction line 28.The cold-producing medium of high pressure from gas cooler 104 shown in Figure 14 is via suction line 28 and suck path 27 guiding suction action chamber 23a.

Suck path 27 (first sucks the path) and be formed on the direction that suction action chamber 23a widens from the suction action chamber 23a part adjacent with the first partition member 24 roughly fan-shaped with circular-arc extension with respect to the opening (suction inlet) 26 of suction action chamber 23a.Suction inlet 26 is only when first piston 21 is positioned on the top dead centre, by first piston 21 complete atresia.And the whole period except the moment that is positioned at top dead centre except first piston 21, at least a portion of suction inlet 26 is exposed suction action chamber 23a.Particularly, see on the plane that the outboard end limit 26a of suction inlet 26 forms circular-arc along the outer peripheral face of the first piston 21 that is positioned at top dead centre.In other words, outboard end limit 26a forms circular-arc with the roughly the same radius of the outer peripheral face of first piston 21.

On the other hand, offer ejection path 30 (the first ejection path) in the part adjacent with the first partition member 24 of spray action chamber 23b.As shown in figure 15, this ejection path 50 also with suck path 27 similarly, be formed on the second inaccessible parts 113.Ejection path 30 is communicated with (with reference to Figure 15) with bleed pipe 31.Thus, the cold-producing medium in the 23b of spray action chamber goes out to evaporimeter 106 side sprays via spraying path 30 and bleed pipe 31.In addition, in Figure 15, bleed pipe 31 is positioned at the paper rear side with respect to suction line 28, so and with Reference numeral 31 and Reference numeral 28, but this record and do not mean that suction line 28 and bleed pipe 31 is made of shared pipe.

The opening with respect to spray action chamber 23b (squit hole) 29 in ejection path 30 forms roughly fan-shaped with circular-arc extension of direction from from the part adjacent with the first partition member 24 of spray action chamber 23b to the expansion of spray action chamber 23b.Squit hole 29 is only when first piston 21 is positioned at top dead centre, by first piston 21 complete atresia.And during whole the moment that is positioned at top dead centre except first piston 21, at least a portion of squit hole 29 is exposed spray action chamber 23b.Particularly, see on the plane that the outboard end limit 29a that is positioned at the squit hole 29 in the outside about the radial direction of the first cylinder body 22 forms circular-arc along the outer peripheral face of the first piston 21 that is positioned at top dead centre.In other words, outboard end limit 29a forms circular-arc with the roughly the same radius of the outer peripheral face of first piston 21.

Like this, power recovery mechanism 105 has the structure roughly the same with the fluid pressure motor of the illustrated rotary type of the embodiment of front.About top dead centre, also as the first embodiment is illustrated.

As mentioned above by form sucking path 27 and ejection path 30, thereby shown in Figure 18 the picture left above (ST1), only be positioned at the moment of top dead centre at first piston 21, both close suction inlet 26 and ejiction opening 29 fully.That is, the first operating chamber 23 forms one moment, and both close suction inlet 26 and ejiction opening 29 fully.In more detail, before moment of being communicated with, suction action chamber 23a is communicated with suction path 27 in suction action chamber 23a and ejection path 30.And suction action chamber 23a is communicated with ejection path 30, and suction action chamber 32a consisted of after the moment of spray action chamber 23b, and suction inlet 26 is closed by first piston 21.Therefore, suppress from sucking path 27 to the suction of the cold-producing medium in ejection path 30.Therefore, realize high efficiency power recovery.

In addition, from the total ban cold-producing medium from sucking path 27 to 30 suctions of ejection path, preferably be positioned at the moment of top dead centre at first piston 21, both close suction inlet 26 and ejiction opening 29.Wherein, even be positioned at the moment of top dead centre at first piston 21, in the situation that only a side of suction inlet 26 and ejiction opening 29 closes, the difference in the moment that the moment that suction inlet 26 is closed and ejiction opening 29 are closed consists of the anglec of rotation of axle 12, if less than about 10 °, then between suction path 27 and ejection path 30, basically do not produce suction.That is, the difference in the moment that the moment that suction inlet 26 is closed and ejiction opening 29 are closed consists of the anglec of rotation of axle 12, by being set as less than about 10 °, aspirates to ejection path 30 from sucking path 27 thereby can suppress cold-producing medium.This and the first embodiment and the second embodiment also are common.

As mentioned above, suction action chamber 23a always is communicated with suction path 27.In addition, spray action chamber 23b always is communicated with ejection path 30.In other words, in power recovery mechanism 105, basically suck continuously the stroke of cold-producing medium and the stroke of the cold-producing medium of this suction of ejection.Therefore, change in volume does not occur and passes through power recovery mechanism 105 in the cold-producing medium of suction basically.

(action of power recovery mechanism 105)

Figure 18 is the schematic diagram of movements of power recovery mechanism 105, the figure of the one of four states of expression ST1～ST4.Can be clear and definite from the contrast of Figure 18 and Fig. 5, about the operating principle of power recovery mechanism 105, can quote the explanation of the fluid pressure motor of the first embodiment.

When first piston 21 rotation, suction inlet 26 is opened, then as Figure 18 (shown in the ST2～ST4), the volume of the cold-producing medium increase suction action chamber 23a by the high pressure that flows into from suction inlet 26.The volume that is accompanied by this suction action chamber 23a enlarges, and the turning moment that imposes on first piston 21 consists of the part of the rotary driving force of axle 12.

Driven force recovering mechanism 105 sees, evaporimeter 106 sides are than gas cooler 104 sides low pressure more.The cold-producing medium of the cryogenic high pressure in the 23b of spray action chamber sucks evaporimeter 106 sides, from spray action chamber 23b to 30 ejections of ejection path.When

spray action chamber

23b and 30 connections of ejection path, begin to spray stroke, then the specific volume of cold-producing medium is anxious increases.Ejection stroke by this cold-producing medium is so that impose on the part that the turning moment of first piston 21 also consists of the rotary driving force of axle 12.That is, the cold-producing medium of axle 12 by high pressure rotates to the attraction of the cold-producing medium of the inflow of suction action chamber 23a and ejection stroke.And, the turning moment of this axle 12 as described later in detail, as the power utilization of booster.

(structure of booster 102)

As shown in figure 15, booster 102 is configured in the top of power recovery mechanism 105 in closed container 111.Power recovery mechanism 105 tops than lower temperature will be configured in than the booster 102 of higher temperatures like this, thereby the heat exchange between booster 102 and the power recovery mechanism 105 can be suppressed.Wherein, also booster 102 can be configured in the below of power recovery mechanism 105.

Booster 102 is connected with power recovery mechanism 105 by axle 12.In the present embodiment, the example that booster 102 is made of the fluid pressure motor of rotary type has been described.Wherein, booster 102 also can by the fluid pressure motor beyond the rotary type for example the fluid pressure motor of vortex shown in Figure 12 consist of.

The basic structure of booster 102 and above-mentioned power recovery mechanism 105 are roughly the same.Particularly, booster 102 has the first inaccessible parts 115 and the 3rd inaccessible parts 114 as shown in figure 15.The first inaccessible parts 115 are common structure members of booster 102 and power recovery mechanism 105.The first inaccessible parts 115 and the 3rd inaccessible parts 114 oppose mutually.Particularly, the face of the opposition side of the face relative with the second inaccessible parts 113 of the 3rd inaccessible parts 114 and the first inaccessible parts 115 is relative.Between the first inaccessible parts 115 and the 3rd inaccessible parts 114, dispose the second cylinder body 42.The inner space that the second cylinder body 42 has general cylindrical shape.The inner space of this second cylinder body 42 is by the first inaccessible parts 115 and the 3rd inaccessible parts 114 obturations.

Axle 12 connects in the second cylinder body 42 at the direction of principal axis of the second cylinder body 42.Axle 12 is configured on the central shaft of the second cylinder body 42.The second piston 41 is configured in by the inner peripheral surface of the second cylinder body 42 and the first inaccessible parts 115 and the 3rd inaccessible parts 114 and divides in the inner space of the general cylindrical shape that forms.The second piston 41 is with respect on the embedded axle 12 under the state of the eccentricity of central axis of axle 12.Particularly, axle 12 has the eccentric part 12c of the central shaft different from the central shaft of axle 12.Embed the second piston 41 of tubular at this eccentric part 12c.Therefore, thus piston 41 with respect to the eccentricity of central axis of the second cylinder body 42.Therefore, eccentric rotary moves thereby piston 41 is followed the rotation of axle 12.

In addition, the eccentric part 12c that the second piston 41 is installed with the roughly the same direction of the eccentric part 12b that first piston 21 is installed on eccentric.Therefore, in the present embodiment, first piston 21 is mutually roughly the same with respect to the eccentric direction of the central shaft of the second cylinder body 42 with respect to eccentric direction and second piston 41 of the central shaft of the first cylinder body 22.

Inner peripheral surface and the first inaccessible parts 115 and the 3rd inaccessible parts 114 by this second piston 41 and the second cylinder body 42 form the second operating chamber 43 (also with reference to Figure 17) in the 42 interior divisions of the second cylinder body.Even the second operating chamber 43 second pistons 41 are with axle 12 rotations, volume does not change basically yet.In addition, " roughly the same " is not only identical situation, and 100 have ± situation of the error of 2～3 ° of degree.

As shown in figure 17, be formed with groove 42a at the line strip of the second operating chamber 43 upper sheds at the second cylinder body 42.Insert sliding freely the second tabular partition member 44 on this lines groove 42a.Dispose force application mechanism 45 between the bottom of the second partition member 44 and lines groove 42a.Pressured towards the outer peripheral face of the second piston 41 by these force application mechanism 45, the second partition members 44.Thus, the second operating chamber 43 is divided into two spaces.Particularly, the second operating chamber 43 is divided into the spray action chamber 43b of on high-tension side suction action chamber 43a and low-pressure side.

In addition, force application mechanism 45 for example can be made of spring.Particularly, force application mechanism 45 can be compression disc spring.

In addition, force application mechanism 45 also can be so-called gas spring etc.Namely, also can be that the second partition member 44 is when when the direction of the volume that dwindles backside space 115 is slided, pressure settings in its backside space 155 be higher than the pressure of the second operating chamber 43, the depended on pressure that acts on to the second piston 41 directions with respect to the second partition member 44 by the pressure differential between this backside space 155 and the second operating chamber 43.For example, also can with backside space 155 as confined space, when the volume of backside space 155 reduces because of retreating of the second partition member 44, apply reaction force to the second partition member 44.In addition, also can be like this, the second partition member 44 is during near the central shaft of axle 12, backside space 155 is not confined space, but when the second partition member 44 when leaving from the second piston 41 to a certain degree, backside space 155 formation confined spaces.Certainly, force application mechanism 45 also can be made of multiple springs such as compression disc spring and gas springs.In addition, the pressure of the second operating chamber 43 is average pressures of the pressure of the pressure of so-called suction action chamber 43a and spray action chamber 43b.Backside space 155 refers to be formed on the space between the bottom of the rear end of the second partition member 44 and lines groove 42a.

On the part adjacent with the first partition member 44 of suction action chamber 43a, as shown in figure 17, offer and suck path 47 (second sucks the path).As shown in figure 15, this suction path 47 is formed on the 3rd inaccessible parts 114 of the downside that is positioned at the second cylinder body 42.Sucking path 47 is communicated with suction line 48.Come the cold-producing medium of flash-pot 106 (with reference to Fig. 1) to import suction action chamber 43a via suction line 48 and suction path 47.

Be formed on the direction that suction action chamber 43a widens from the part adjacent with the second partition member 44 of suction action chamber 43a roughly fan-shaped with circular-arc extension at the opening with respect to suction action chamber 43a (suction inlet) 46 that sucks path 47.Suction inlet 46 is only when the second piston 41 is positioned on the top dead centre, by the second piston 41 complete atresia.And the whole period except the moment that is positioned at top dead centre except the second piston 41, at least a portion of suction inlet 46 is exposed suction action chamber 43a.Particularly, see on the plane that the outboard end limit 46a that is positioned at the suction inlet 46 in the outside about the radial direction of the second cylinder body 42 forms circular-arc along the outer peripheral face of the second piston 41 that is positioned at top dead centre.In other words, outboard end limit 46a forms circular-arc with the roughly the same radius of the outer peripheral face of the second piston 41.

On the other hand, offer ejection path 50 (the second ejection path) on the part adjacent with the second partition member 44 of spray action chamber 43b.As shown in figure 15, this ejection path 50 also with suck path 47 similarly, be formed on the 3rd inaccessible parts 114.Ejection path 50 is communicated with bleed pipe 151.Thus, the cold-producing medium in the 43b of spray action chamber goes out to compressor 103 side sprays via ejection path 50 and bleed pipe 151 2.In addition, among Figure 15, bleed pipe 151 is positioned at the paper rear side with respect to suction line 48, so and with Reference numeral 151 and 48, but this record and do not mean that pipe formation by being shared with suction line 48 and bleed pipe 151.

Ejection path 50 is connected with backside space 155 via communication path 156.Particularly, in the present embodiment, this communication path 156 is communicated with backside space 155 during near the central shaft of axle 12 when the second partition member 44.Communication path 156 when the second partition member 44 when leaving to a certain degree the central shaft of axle 12, then stopped up by the second partition member 44.Namely, the second partition member 44 near the progressive position of the central shaft of axle 12 during slide away from the going-back position of the central shaft of axle 12, communication path 156 is from opening state to closing state variation, and backside space 155 changes to the confined space that covers with communication path 156 from the open space that is communicated with communication path 156.Therefore, stop up communication paths 156 by the second partition member 44, after backside space 155 became confined space, backside space 155 was as gas spring, pressured the second partition member 44 on the second piston 41 directions.

The opening with respect to spray action chamber 43b (ejiction opening) 49 in ejection path 50 is formed on the direction that suction action chamber 43a widens from the part adjacent with the second partition member 44 of suction action chamber 43a roughly fan-shaped with circular-arc extension.Suction inlet 49 is only when the second piston 41 is positioned on the top dead centre, by the second piston 41 complete atresia.And the whole period except the moment that is positioned at top dead centre except the second piston 41, at least a portion of suction inlet 49 is exposed suction action chamber 43b.Particularly, see on the plane that the outboard end limit 49a that is positioned at the ejiction opening 49 in the outside about the radial direction of the second cylinder body 42 forms circular-arc along the outer peripheral face of the second piston 41 that is positioned at top dead centre.In other words, outboard end limit 49a forms circular-arc with the roughly the same radius of the outer peripheral face of the second piston 41.

About the top dead centre of the second piston 41, also quote the explanation in the first embodiment.

As mentioned above by form sucking path 47 and ejection path 50, thereby shown in Figure 19 the picture left above, only be positioned at the moment of top dead centre at the second piston 41, both close suction inlet 46 and ejiction opening 49 fully.That is, the first operating chamber 43 forms one moment, and both close suction inlet 46 and ejiction opening 49 fully.That is, consist of one moment in the second operating chamber 43, both close suction inlet 46 and ejiction opening 49 fully.In more detail, before suction action chamber 43a and moment that ejiction opening 49 is communicated with, suction action chamber 43a with suck path 47 and be communicated with.And suction action chamber 43a is communicated with ejection path 50, and suction action chamber 42a consisted of after the moment of spray action chamber 43b, and suction inlet 46 is closed by the second piston 41.Therefore, suppress cold-producing medium to the adverse current in the lower suction path 47 of pressure ratio.Therefore, realize high efficiency mistake to.As a result, can improve the utilization ratio of the power that is recovered.

In addition, from limiting cold-producing medium fully from sucking path 50 to the viewpoint of ejection path 47 suctions, preferably be positioned at the moment of top dead centre at the second piston 41, both close suction inlet 47 and ejection path 50.Wherein, even be positioned at the moment of top dead centre at the second piston 41, in the situation that only a side of suction inlet 46 and ejiction opening 49 closes, the difference in the moment that the moment that suction inlet 46 is closed and ejiction opening 49 are closed consists of the anglec of rotation of axle 12, if less than about 10 °, then in fact do not produce the adverse current from ejection path 50 to the cold-producing medium that sucks path 47.That is, the difference in the moment that the moment that suction inlet 46 is closed and ejiction opening 49 are closed consists of the anglec of rotation of axle 12, by being set as less than about 10 °, thereby can suppress cold-producing medium from ejection path 50 to the adverse current that sucks path 47.

In addition, as mentioned above, suction action chamber 43a always is communicated with suction path 47.In addition, spray action chamber 43b always is communicated with ejection path 50.In other words, in booster 102, basically suck continuously the stroke of cold-producing medium and the stroke of the cold-producing medium of this suction of ejection.Therefore, the cold-producing medium of suction there is no change in volume and passes through booster 102.

(action of booster 102)

Then, describe the operating principle of booster 102 in detail with reference to Figure 19.The figure that represents the one of four states of T1～T4 among Figure 19.Contrast according to Figure 19 and Fig. 5 can be clear and definite, about the operating principle of booster 102, can quote the explanation of the fluid pressure motor of the first embodiment.

The dynamic rotation of axle 12 by being reclaimed by power recovery mechanism 105.With the rotation of this axle 12, the second piston 41 also rotates, and drives booster 102.

The second operating chamber 43 basically its volume is constant.Suction action chamber 43a always is communicated with suction path 47.Spray action chamber 43b always is communicated with ejection path 50.Therefore, in the second operating chamber 43 of booster 102, cold-producing medium is not also expansion useless of compression both.Axle 12 is by 105 rotations of power recovery mechanism, and booster 102 is driven, and correspondingly, the downstream of the second operating chamber 43 forms high pressure than the upstream side of the second operating chamber 43.In other words, by the power-actuated booster 102 to be reclaimed by power recovery mechanism 105, the pressure of evaporimeter 106 sides of the pressure ratio suction inlet 46 of compressor 103 sides of ejiction opening 49 is high.That is, boost by booster 102.

In addition, in the present embodiment, it is roughly consistent that the second piston 41 that the first piston 21 of power recovery mechanism 105 is positioned at moment of top dead centre and booster 102 is positioned at moment of top dead centre.

(counterweight 152)

As shown in figure 15, be provided with counterweight 152 at fluid machinery 110.Particularly, counterweight 152a and counterweight 152b are installed in the end of axle 12.In addition, in this manual, counterweight 152a and counterweight 152b are generically and collectively referred to as counterweight 152.

The weight around the rotating shaft of axle 12 of the rotary body 153 of the second piston 41 that counterweight 152 is installed with the state of off-centre for reducing the first piston 21 that has axle 12, install with eccentric state with respect to axle 12, with respect to axle 12 is uneven.Particularly, even for the weight balancing around rotating shaft of the axle 12 that makes rotary body 153.

Particularly, each of

counterweight

152a and 152b forms the cylindrical of centered by the central shaft of axle 12 axle as shown in figure 20.That is, the shape separately (outer shape) of

counterweight

152a and 152b is axial symmetry with respect to the rotating shaft of axle 12.On the other hand, see circular-arc inner space 154 on each plane that is formed with centered by the central shaft of axle 12 of counterweight 152a and 152b.Therefore, each central shaft around axle 12 of

counterweight

152a and 152b has the weight inequality.And as shown in figure 15,

counterweight

152a and 152b install with respect to axle 12 in the part mode heavier than the part that is positioned at a side consistent with above-mentioned eccentric direction that it is positioned at the opposite side of eccentric direction of first piston 21 and the second piston 41.That is,

counterweight

152a and 152b are installed on the axle 12 than the mode that the central shaft of axle 12 more is positioned at the eccentric direction side of first piston 21 and the second piston 41 with its part that forms inner space 154.

In addition, form separately the intercommunicating pore 157 be communicated with inner space 154 at counterweight 152a and 152b.This is be used to making the lubricant that fills up in the closed container 111 that describes in detail later flow into inner space 154.

-compressor 103-

Figure 21 is the ideograph of the schematic configuration of expression compressor 103.Compressor 103 has compressing mechanism 103a, motor 108, takes in their housing 160.Be formed with the oily storage unit 161 of storing frozen machine oil in the bottom of housing 160.In this oil storage unit 161, dispose fluid pump 162.Draw the refrigerator oil that is stored on the oily storage unit 161 by this fluid pump 162, supply with compressing mechanism 103a.

In the present embodiment, as shown in figure 21, compressor 103 is configured in than on the high position of fluid machinery 110.And, connecting oil equalizing pipe 163 in oily storage unit 161.In addition, this oil equalizing pipe 163 is connected with closed container 111.At oil equalizing pipe 163 throttle mechanism 164 is installed.By the pressure in these throttle mechanism 164 adjustment housings 160 and the pressure in the closed container 111.Particularly, by this throttle mechanism 164 pressure in the closed container 111 is adjusted into less than the pressure in the housing 160.More specifically, make pressure in the closed container 111 be adjusted into pressure between the pressure of low-pressure side of the on high-tension side pressure of refrigerant loop 109 and refrigerant loop 109 by throttle mechanism 164.In other words, the pressure setting in the closed container 111 is the pressure greater than the low-pressure side of refrigerant loop 109, less than the on high-tension side pressure of refrigerant loop 109.

-freeze cycle-

The freeze cycle of freezing cycle device 101 then, is described with reference to Figure 22.Figure 22 is the Mollier line chart identical with Fig. 6.Among Figure 22, h _A, h _B, h _C, h _D, h _EThe heat content that represents respectively the cold-producing medium of A, B, C, D, E each point.

The closed loop of ABCDE among Figure 22 represents the freeze cycle of the freezing cycle device 101 of power recovery type shown in Figure 14.A-B in the ABCDE closed loop represents the state variation of the cold-producing medium of booster 102.B-C represents the state variation of the cold-producing medium of compressing mechanism 103a.C-D represents the state variation of the cold-producing medium of gas cooler 104.D-E represents the state variation of the cold-producing medium of power recovery mechanism 105.E-A represents the state variation of the cold-producing medium of evaporimeter 106.

In compressing mechanism 103a, cold-producing medium is by above-critical state (some C) compression from the gaseous state of low-temp low-pressure (some B) to HTHP.The cold-producing medium that compresses among the compressing mechanism 103a is cooled off liquid (some D) by the above-critical state from gas cooler 104 (some C).In addition, the temperature and pressure of the cold-producing medium of some B is slightly higher than the temperature and pressure of some A.

Afterwards, cold-producing medium expands (pressure drop) to gas-liquid two condition (putting E) via saturated solution (some S) from the liquid state (some D) of cryogenic high pressure in power recovery mechanism 105.In the stroke of this pressure decreased (expansion), cold-producing medium is incompressible liquid state from a D to a S, so the specific volume of cold-producing medium does not almost change.On the other hand, cause the pressure drop of following specific volume pressure drop jumpy namely to follow expansion to the metamorphosis from the liquid state to the gaseous state the E from a S.

Cold-producing medium from power recovery mechanism 105 is heated in evaporimeter 106, and (some A) changes from gas-liquid two condition (some E) to gaseous state when being accompanied by evaporation.The cold-producing medium that is heated by evaporimeter 106 boosts and changes to gaseous state (some B) at booster 102.

-effect-

As mentioned above, in the present embodiment in, reclaim power by power recovery mechanism 105.The power that is reclaimed by power recovery mechanism 105 is as the power utilization of booster 102.Therefore, can realize high efficiency.Particularly, use Figure 22 to describe, then in power recovery mechanism 105, as with respect to (h _D-h _E) function as power from refrigerant-recovery.Large budgetary estimate is equivalent to the heat content (h of this recovery _D-h _E) multiply by the efficiency eta of power recovery mechanism 105 _ExpEfficiency eta with booster 102 _PumpAnd the heat content η that obtains _Expη _Pump(h _D-h _E)=(h _B-h _A) energy by booster 102 the supply system cryogens.As a result, cold-producing medium is boosted to a B from some A shown in Figure 22.

For example, in the freezing cycle device that does not dispose booster 102, compressing mechanism 103a is compressed to cold-producing medium the point C of the entrance side of gas cooler 104 from the some A of the outlet side of evaporimeter 106.With respect to this, in the freezing cycle device 101 in the present embodiment that is provided with the booster 102 that is connected with power recovery mechanism 105, pass through booster 102 by making cold-producing medium, and cold-producing medium is boosted to a B from an A.Therefore, compressing mechanism 103a is as long as be compressed to a C from a B.Therefore, the workload of compressing mechanism 103a can be to be equivalent to (h _B-h _A) energy reduce.As a result, can improve the COP of freezing cycle device 101.

In addition, for example also consider use decompressor in the past as power recovery mechanism 105.Use as power recovery mechanism 105 in the situation of decompressor in the past, can reclaim the energy that the pressure differential of energy that the expansion of cold-producing medium causes and suction side and ejection side causes.With respect to this, the fluid pressure motor does not make cold-producing medium expand in inside.Therefore, shown in present embodiment, use as power recovery mechanism 105 in the situation of fluid pressure motors, only can reclaim the energy that the pressure differential of suction side and ejection side causes.Therefore, from the appearance, use decompressor in the past can improve efficiency as power recovery mechanism 105.

But illustrated in the first embodiment such as reference Fig. 8, power recovery mechanism 105 uses the fluid pressure motor can improve on the contrary the efficiency of freezing cycle device 101.Particularly, in the freezing cycle device that uses the such volume supercritical refrigerant of carbon dioxide, do not have intrinsic specific volume the fluid pressure motor to use the viewpoint in the reduction that prevents the efficient that the overexpansion loss brings be outstanding.

In addition, in the present embodiment, power recovery mechanism 105 and booster 102 and the compressor that needs pilot valve etc. and decompressor etc. relatively then are made of the relatively simple fluid pressure motor of structure.Particularly, in the present embodiment, power recovery mechanism 105 and booster 102 also are made of the fluid pressure motor of rotary type relatively simple for structure in the fluid pressure motor.Therefore, freezing cycle device 101 that can the simple realization cheapness.

For example, shown in the JP 2006-266171 communique described above, also consider to replace booster 102 and the configuration auxiliary compressor.But auxiliary compressor is compared with booster 102, and structure is very complicated, and manufacturing cost is high.Therefore, if use auxiliary compressor, the then complex structure of freezing cycle device 101.In addition, the manufacturing cost of freezing cycle device 101 rises.

In addition, using in the situation of booster 102 as booster, also can expect the equal result identical with the situation of using auxiliary compressor as booster.Below, describe its reason in detail with reference to Figure 23.

Figure 23 is the curve map of the relation of the specific volume of cold-producing medium of expression booster 102 and compressing mechanism 3a and pressure.Among Figure 23, the some A, the some B, the some C respectively with Figure 22 in some A, the some B, the some C corresponding.In addition, Figure 23 represents that freezing cycle device 101 is for the result of the computer simulation of the situation of hot-warer supplying machine.The pressure of point A is 3.96Mpa.The temperature of point A is 10.7 ℃.The pressure of point B is 4.36MPa.The pressure of point C is 9.77Mpa.Between some A and the some B and some B and some the heat content such as be assumed between the C.

As shown in figure 23, come the cold-producing medium of flash-pot 106 at first to be inhaled into booster 102.And in booster 102, cold-producing medium is boosted to a B from an A.Say that closely booster 102 can basically change in volume not occur and spray cold-producing medium.And, by the cold-producing medium of sending booster 102 cold-producing medium is boosted.As the situation of the auxiliary compressor that boosts, the state of cold-producing medium can directly not change to a B from an A therefore.When cold-producing medium moves from suction action chamber 43a to spray action chamber 43b, keep specific volume constant, boost to an O from an A.Afterwards, when spraying from spray action chamber 43b, change to the specific volume identical with the cold-producing medium of the suction side of compressing mechanism 103a from an O to a B equipressure.

At this, the area of the part of being surrounded by the NCBOALM of Figure 23 is equivalent to compress the theoretical value of the required work done of the cold-producing medium of unit mass.The complete theoretical compression work done W that the area of the part of surrounding with this NCBOALM is suitable _C0Theory compression work done W by booster 102 _C1Theory compression work done W with compressing mechanism 103a _C2Aggregate value represent.In addition, the theory of booster 102 compression work done W _C1Work done W by heat insulation compression (AB) _C11With the work done W that compares increase with heat insulation compression _C12Aggregate value represent.At this, the efficiency eta of power recovery mechanism 105 _ExpBe 81%, the efficiency eta of booster 102 _PumpWhen being 81%, then in model shown in Figure 23, W in fact _C1Be W _C0(=W _C1+ W _C2) 10%.W _C2Be W _C090%.W _C12Be W _C14%.W _C12Be W _C00.4%.

Like this, replace auxiliary compressor and use the increase W of work done of the situation of booster 102 _C12Few.In addition, the shared complete theoretical compression work done W of work done _C0Recruitment W _C12Ratio be negligible level almost.Therefore, using in the situation of booster 102 as booster, also can realize high energy efficiency.

In addition, use in the situation of booster 102 pressure loss that does not cause because of the ejection valve etc.Therefore, the situation as booster use booster 102 is compared to the situation that booster uses auxiliary compressor, can realize relatively high efficiency.

In addition, for example replace booster 102 and the configuration auxiliary compressor, in the situation as power recovery mechanism configuration decompressor, by the recovery torque of decompressor recovery and the load torque of adding in auxiliary compressor, waveform is mutually different.In other words, during a cycle in, reclaim the rate of change of torque and load torque.Reclaim torque to the rotating speed increase of the large then axle of ratio change of load torque.On the other hand, diminish for the ratio of load torque if reclaim torque phase, then the rotating speed of axle reduces.That is, during a cycle in, it is regional to produce the anglec of rotation that the rotating speed of anglec of rotation zone that the rotating speed of axle increases and axle reduces.Therefore, the rotation of axle becomes and has some setbacks.In addition, the organic efficiency of energy also reduces.

Replace booster 102 and the configuration auxiliary compressor, in the situation as power recovery mechanism fluid pressure motor, also can with above-mentioned situation similarly, can not fully suppress uneven for the rotating speed of the axle of the rate of change of load torque based on reclaiming torque phase.

In the fluid pressure motor, suction stroke and ejection stroke carry out continuously.In addition, the pressure of suction action chamber equate with the pressure of suction side, constant.On the other hand, the pressure of spray action chamber with the ejection side pressure equate, constant.Like this, it is always constant to act on the pressure of piston.Therefore, reclaim torque phase and be sine wave roughly for the waveform of the rotation of axle.

With respect to this, in auxiliary compressor, operating chamber is isolated from sucking the path and spraying the path, betwixt compressed refrigerant.Therefore, the constant pressure of suction action chamber, but in compression travel, the pressure rise of operating chamber.Therefore, load torque does not consist of sine wave with respect to the waveform of the rotation of axle.

Like this, replace booster 102 and the configuration auxiliary compressor, in the situation as power recovery mechanism fluid pressure motor, the waveform that reclaims torque and load torque is mutually different.As a result, the abundant smooth and easy running of realization axle is difficult.

In addition, configuration booster 102, the situation of using decompressor as power recovery mechanism is too.Use decompressor as power recovery mechanism, then reclaim torque phase and do not consist of sine wave for the waveform of the rotation of axle.With respect to this, because booster 102 be the fluid pressure motor, so load torque is sine wave roughly with respect to the waveform of the rotation of axle.Like this, in this case, also be that the waveform of recovery torque and load torque is mutually different.As a result, the abundant smooth and easy running of realization axle is difficult.

With respect to this, in the present embodiment in, interconnective booster 102 and power recovery mechanism 105 each free fluid pressure motor consist of.Therefore, shown in Figure 24 A and Figure 24 B, the waveform of the waveform of the recovery torque of being reclaimed by power recovery mechanism 105 and the load torque of booster 102 is seemingly closer.Particularly, reclaiming the waveform of torque and the waveform of load torque is similar shape at the y direction of expression recovery torque.And the waveform of recovery torque and the waveform both sides of load torque are the 360 ° of sine waves as one-period of the anglec of rotation take axle 12.Like this, the ratios constant of load torque and recovery torque.Particularly, it is large that load torque becomes, and then reclaims torque and also become large.Load torque diminishes, and then correspondingly, reclaims torque and also diminishes.As a result, axle 12 does not slow down, and can rotate swimmingly.Like this, the organic efficiency of function improves.In addition, the generation of vibration and noise is suppressed.

Particularly, it is synchronous that the piston that is positioned at moment of top dead centre and booster 102 by the piston that makes power recovery mechanism 105 is positioned at moment of top dead centre, thereby the waveform that can make the waveform of load torque and reclaim torque coincide mutually.In other words, on any anglec of rotation of axle 12, the ratio of load torque and recovery torque all is constant basically.The rotary speed inequality that therefore, can suppress axle.As a result, can further improve the efficiency of freezing cycle device.In addition, because it is uneven to suppress the rotary speed of axle, so vibration and noise that also can the freezing-inhibiting EGR.

More specifically, in the present embodiment, with respect to the direction of axle 12 configuration the first partition member 24 and mutually roughly the same with respect to the direction of axle 12 configurations the second partition member 44.In addition, first piston 21 is mutually roughly the same with respect to the eccentric direction of the central shaft of the second cylinder body 42 with respect to eccentric direction and second piston 41 of the central shaft of the first cylinder body 22.Thus, the moment that the piston that makes piston by power recovery mechanism 105 be positioned at moment of top dead centre and booster 102 is positioned at top dead centre is (consistent) synchronously.Eccentric part 12b, the 12c of axle 12 is oriented identical structure, and compares for different structures, makes easily fluid machinery 110.

In addition, by making first piston 21 also mutually roughly the same with respect to the eccentric direction of the central shaft of the second cylinder body 42 with respect to eccentric direction and second piston 41 of the central shaft of the first cylinder body 22, thereby can reduce axle 12, axle holds the second inaccessible parts 113 of this axle 12 and the frictional force between the 3rd inaccessible parts 114.

First piston 21 effect of power recovery mechanism 105 from than the suction action chamber 23a of higher pressure towards the pressure differential of the direction of the spray action chamber 23b of low pressure relatively.Similarly, the second piston 41 effect of booster 102 from than the spray action chamber 43b of higher pressure towards the pressure differential of the suction action chamber 43a of low pressure relatively.These pressure differentials act on axle and hold the second inaccessible parts 113 of axle 12 and the bearing portion of the 3rd inaccessible parts 114 via the pressured axle 12 of eccentric part 12b, 12c.As a result, produce rotation obstruction power with respect to axle 12, promote the abrasion of axle 12, the abrasion of bearing portion.

Consider such problem, in the present embodiment, adopt mutually reverse structure of the pressure differential that acts on first piston 21 and the pressure differential that acts on the second piston 41.Shown in Figure 24 C, in power recovery mechanism 105, act on the pressure differential F of first piston 21 ₁Area S for first piston 21 ₁Multiply by suction pressure P _EsWith the ejection pressure P _EdThe value of difference.In booster 102, act on the pressure differential F on the second piston 41 ₂The area S2 that is the second piston 41 multiply by the ejection pressure P _CdWith suction pressure P _CsThe value of difference.With pressure differential F ₁With pressure differential F ₂Projection at grade, then they can be cancelled out each other.When two

pistons

21,41 eccentric direction equate with offset, about direction of principal axis, pressure differential F ₁With pressure differential F ₂Application point consistent, cancel out each other more reliably.

Between first piston 21 and the second piston 41, the result that pressure differential is offset can reduce friction ratio between axle 12 and the second inaccessible parts 113 and the friction ratio between axle 12 and the 3rd inaccessible parts 114.Like this, can reduce the power that makes the required necessity of axle 12 rotations, can improve energy and reclaim.In addition, the abrasion of axle 1, the second inaccessible parts 113 and the 3rd inaccessible parts 114 are also suppressed.

Wherein, form in the situation of above-mentioned structure, comprise first piston 21 and the second piston 41 rotary body 153, exist uneven around the weight balancing of the central shaft of axle 12.Particularly, the eccentric direction side of first piston 21 and the second piston 41 is heavier.On the other hand, a side opposite with eccentric direction is low weight.In the present embodiment, uneven for the weight around the central shaft of axle 12 that reduces this rotary body 153, at axle 12 two

counterweight

152a, 152b are installed.By these two

counterweight

152a, 152b, the weight around the central shaft of axle 12 that reduces rotary body 153 is uneven.In the present embodiment, particularly the weight balancing around the central shaft of axle 12 of rotary body 153 is uniform.Therefore, realize the smoothly rotation of rotary body 153.In addition, the vibration the during rotation of rotary body 153 is suppressed, and reduces vibration and the noise of freezing cycle device 101.In addition, from the viewpoint of the vibration of effective reduction rotary body 153, it is feasible disposing at least counterweight 152 at each two ends of axle 12.Wherein, also can on the basis of

counterweight

152a, 152b, at axle 12 one or more counterweights be installed again.

Such as Figure 15 and shown in Figure 20, the shape separately of

counterweight

152a, 152b is axial symmetry with respect to the rotating shaft of axle 12.Therefore

counterweight

152a, 152b be not because of the rotation displacement of axle 12.In other words, though the anglec of rotation of the shape axle 12 in the shared space of

counterweight

152a, 152b how and be constant.For example, in the situation of counterweight 152a, the 152b displacement by the rotation of axle 12, rotate by making

counterweight

152a, 152b, thus the refrigerator oil in the stirring closed container 111.As a result, low-energy organic efficiency falls in the produce power loss.With respect to this, in the present embodiment, the shape separately of

counterweight

152a, 152b is axial symmetry with respect to the rotating shaft of axle 12.Therefore, though

counterweight

152a, 152b rotation, with the refrigerator oil that can not stir very much in the closed container 111.Therefore, the energy loss that causes of

counterweight

152a, 152b rotation is suppressed.As a result, realization can high organic efficiency.

In addition, shown in present embodiment, preferably see circular-arc inner space 154 when the plane that forms centered by the central shaft of axle 12 in columniform main body, thereby the rotating shaft around axle 12 forms in the situation of weight inequality, so that refrigerator oil imports the mode of inner space 154, the intercommunicating pore 157 that is communicated with inner space 154 in advance.

In addition, from the viewpoint of the quantity that reduces counterweight 152 etc., also can make first piston 21 mutually different with respect to the eccentric direction of the central shaft of the second cylinder body 42 with the second piston 41 with respect to the eccentric direction of the central shaft of the first cylinder body 22.For example can make first piston 21 differ 180 ° with respect to the eccentric direction of the central shaft of the first cylinder body 22 and the second piston 41 with respect to the eccentric direction of the central shaft of the second cylinder body 42.

Wherein, heavy with fluid machinery 110 or the compressing mechanism 103a of High Rotation Speed at axle 12, in order to suppress the abrasion of sliding part, sliding part is supplied with refrigerator oil.In the present embodiment, be frozen machine oil in the closed container 111 of fluid machinery 110 and fill up.And this refrigerator oil infiltrates each sliding part, and each sliding part is lubricated.Therefore, can supply with reliably refrigerator oil to each sliding part.As the supply method of refrigerator oil, shown in compressor 103, consider to use fluid pump the sliding part of compressing mechanism 103a to be supplied with the method for refrigerator oil.But, in this case, if producing the liquid level of fault or refrigerator oil, reduces fluid pump, and then can worry and can not supply with the fully refrigerator oil of amount to each sliding part.With respect to this, shown in present embodiment, filled up by refrigerator oil if make in the closed container 111, power recovery mechanism 105 and booster 102 direct impregnation in refrigerator oil, then with respect to each sliding part, can be supplied with the refrigerator oil of abundant amount reliably.

In addition, be equipped with in the situation of compressing mechanism 103a of motor 108, it is undesirable that housing 160 is filled up by refrigerator oil.If the insulating properties of refrigerator oil is insufficient, then motor 108 can suffer damage.On the other hand, in the situation of closed container 111, because inside do not take in electronic unit, so the problem such as infringement not.

In addition, in the present embodiment, storing relatively, the compressor 103 of the refrigerator oil of volume is configured on the position that is higher than fluid machinery 110.And, be provided with the oily storage unit 161 of connection compressor 103 and the oil equalizing pipe 163 in the closed container 111.Therefore, if the amount of the refrigerator oil in the closed container 111 reduces, then via oil equalizing pipe 163 from 161 pairs of closed container 111 automatic makeups of oily storage unit of compressor 103 to refrigerator oil.In addition, return the oily storage unit 161 of compressor 103 via the refrigerant piping of refrigerant loop 109 to the refrigerator oil of power recovery mechanism 105 and booster 102 fuel feeding.Therefore, the amount that is stored in the refrigerator oil in the oily storage unit 161 of compressor 103 can always be kept roughly a certain amount of.

In addition, at oil equalizing pipe 163 throttle mechanism 164 is installed.By this throttle mechanism 164, can adjust refrigerator oil to the flow of closed container 111 and the pressure in the closed container 111.

In addition, the temperature of being prepared the cold-producing medium that boosts by booster 102 is lower, so in the fluid machinery 110 of Figure 15, be difficult to cause heat exchanger between booster 102 and power recovery mechanism 105.This heat exchange amount is less than the heat exchange amount of the structure (structure of the first embodiment) that connects power recovery mechanism 105 and compressing mechanism 103a.Therefore, the mechanism that consists of high temperature when suppressing heat from action moves to forming low temperature, and in the viewpoint that improves efficiency, the structure that connects power recovery mechanism 105 and booster 102 is more favourable than the first embodiment.

In addition, in the present embodiment, power recovery mechanism 105 and booster 102 are accommodated in the closed container 111.Thus, power recovery mechanism 105 and booster 102 have been realized the freezing cycle device 101 of compression by compact compression.In addition, in the present embodiment, the first inaccessible parts 115 are by booster 102 and the 105 common uses of power recovery mechanism, so can realize the compact freezing cycle device 111 of special compression.In addition, in the present embodiment, both are formed on the second inaccessible parts 113 to suck path 27 and ejection path 30.On the other hand, suck path 47 and be formed on the 3rd inaccessible parts 114 with ejection path 50.Like this, by will sucking path 27 (47) and ejection path 30 (50) is formed on the inaccessible parts of the same side, thereby thickness that can thinning the first inaccessible parts 115 is realized the further densification of fluid machinery 110.For example, any that sucks path 27, ejection path 30, sucks path 47 and ejection path 50 is formed on the first inaccessible parts 115, then correspondingly has to thicken the thickness of the first inaccessible parts 115.As a result, fluid machinery 110 maximizes.In addition, from the viewpoint of the densification of fluid machinery 110, also can will suck path 27, ejection path 30, suck path 47 and ejection path 50 all be formed on the first inaccessible parts 115.

Wherein, the force application mechanism 45 of pressured the second partition member 44 is springs of being located at the compression on the narrow backside space 155.Therefore, according to operating condition, the application of force power of force application mechanism 45 can be not enough.If the application of force power of force application mechanism 45 is not enough, then suction action chamber 43a links to each other with spray action chamber 43b, causes the suction of cold-producing medium.As a result, energy recovery efficiency reduces.Therefore, preferably make the pressure of pressure ratio the second operating chamber 43 in the backside space 155 large, the pressure of the second partition member 44 pressured the second pistons 41 is kept higher than the pressure of the second operating chamber 43.

On the other hand, the pressure of the second partition member 44 pressured the second pistons 41 is higher, and then the sliding friction of the second partition member 44 and the second piston 41 is also larger.As a result, the friction of the second partition member 44 and the second piston 41 becomes fierce.Therefore, the pressure of the second partition member 44 pressured the second pistons 41 preferred utmost point low value in the scope of the pressure that is higher than the second operating chamber 43.

In the present embodiment, be formed with at cylinder body 42 and be communicated with backside space 155 and than the communication path 156 in the ejection path 50 of higher pressure.Therefore, the pressure in the backside space 155 and ejection path 50 interior pressure equate.Therefore, backside space 155 is as so-called gas spring effect, and the pressure of the second partition member 44 pressured the second pistons 44 can always be kept the pressure that is higher than the second operating chamber 43.As a result, suppress the suction of cold-producing medium, can further improve the efficiency of freezing cycle device 101.

In addition, booster 102 is owing to being the fluid pressure motor, so the pressure differential of suction action chamber 43a and spray action chamber 43b is so large.Therefore, the pressure of backside space 155 can be so not high.Therefore, if to applying superfluous pressure between the second partition member 44 and the second piston 41, then suppress the abrasion of the second partition member 44 and the second piston 41.From the viewpoint of the abrasion between special establishment the second partition member 44 and the second piston 41, the pressure in the pressure ratio closed container 111 in the backside space 155 is low to be particularly preferred.

Wherein, the power of the second partition member 44 being bestowed with respect to the second piston 41 is when the second partition member 44 leaves the central shaft of axle 12 most in the time of the most necessary.That is, the second piston 41 is positioned at top dead centre, when the rotation direction of the second partition member 44 changes.This be because, before the second piston 41 arrives top dead centre, the second partition member 44 is pressured by the second piston 41, but the second piston 41 arrives after top dead center, the position of part that the side face of the second piston 41 contacts the second partition member 44 is during near the central shaft of axle 12, the second piston 41 is by after top dead center, and the pressure between the second piston 41 and the second partition member 44 has the tendency of reduction.

On the other hand, the second piston 41 during near the central shaft of axle 12, when namely the second piston 41 is positioned at lower dead center, need not apply so large application of force power to the second partition member 44 at the second partition member.This is because when the second piston 41 arrived lower dead center, 44 beginnings of the second partition member were pressured by the second piston 41.

Therefore, preferred communication path 156 when the second partition member 44 when the direction of the volume that dwindles backside space 155 is slided, formed by 44 lockings of the second partition member.That is, backside space 155 consisted of confined space when preferred the second partition member 44 slided in the direction of the volume that dwindles backside space 155, formed so-called gas spring.Accordingly, when the second piston 41 that needs most when the power of bestowing with respect to the second piston 41 as the second partition member 44 was positioned at top dead centre, the effect of the second partition member 44 by gas spring was towards the second piston 41 application of forces.Therefore, even when the second piston 41 is positioned at top dead centre, also the pressure between the second partition member 44 and the second piston 41 can be kept higher.As a result, suction from suction action chamber 43a to spray action chamber 43b that can the cold-producing medium of establishment from.

" variation 1 "

In the above-described embodiment, the example that backside space 155 is communicated with ejection path 50 by communication path 156 has been described.But, as shown in figure 25, also can by the application of force power of force application mechanism 45, be communicated with suction path 47 and backside space 155 by communication path 156.

In the present embodiment, backside space 155 is owing to is communicated with the suction path 47 of low pressure relatively, thus with the situation of above-mentioned embodiment relatively, the pressure step-down in the backside space 155.Therefore, second partition member 44 and the pressure (act on the load of contact) second piston 41 between of the second piston 41 when lower dead center is less than the situation of above-mentioned embodiment.Therefore, in present embodiment 1 particularly preferably, the second partition member 44 when the direction of the volume that dwindles backside space 155 is slided, by the second partition member 44 locking communication paths 156, can obtaining reliably the effect of gas spring,

" variation 2 "

In addition, also can with backside space 155 in confined space 111 interior connections, be formed at the identical pressure of pressure in the closed container 111.And, also can adjust pressure in the closed container 111 and the pressure in the backside space 155 by adjusting throttle mechanism shown in Figure 21 164.In this case, the suction of the cold-producing medium of the high side to low side from inhibition from booster 102, and the pressure in the viewpoint that suppresses the excessive friction of the second partition member 44 and the second piston 41, closed container 111 and the pressure of backside space 155 are preferably between the pressure of the on high-tension side pressure of refrigerant loop 109 and low-pressure side.

" variation 3 "

In addition, backside space 155 also can form confined space.In this case, the pressure of pressure ratio the second operating chamber 43 in the preferred backside space 155 is high.Pressure in the backside space 155 are preferably below the pressure in the closed container 111.

" variation 4 "

The viewpoints that reduce from the quantity of counterweight 152 etc. also can make first piston 21 mutually different with respect to the eccentric direction of the central shaft of the second cylinder body 42 with the second piston 41 with respect to the eccentric direction of the central shaft of the first cylinder body 22.Particularly from the viewpoint of the quantity that reduces counterweight 152, preferably make first piston 21 differ 180 ° with respect to the eccentric direction of the central shaft of the first cylinder body 22 and the second piston 41 with respect to the eccentric direction of the central shaft of the second cylinder body 42.

In addition, first piston 21 with respect to the first cylinder body 22 the eccentric direction of central shaft mutually different with respect to the eccentric direction of the central shaft of the second cylinder body 42 with the second piston 41, thereby when the starting of freezing cycle device 101, start easily power recovery mechanism 105 and booster 102.

When freezing cycle device 101 stopped, the pressure of the integral body of refrigerant loop 109 equated.If during starting compressor 103, then the suction side of compressor 103 is the interior pressure decreased of pipe arrangement between compressor 103 and the booster 102.On the other hand, the ejection side of compressor 103 is the pressure rise of the pipe arrangement between compressor 103 and the power recovery mechanism 105.Therefore, the pressure differential between the suction side by compressor 103 and the ejection side of compressor 103, both produce starting torque in booster 102 and power recovery mechanism 105.By this starting torque, booster 102 and the 105 beginning automatic control rotations of power recovery mechanism.

For example, first piston 21 with respect to the first cylinder body 22 eccentric direction and second piston 41 of central shaft with respect to the identical situation of the eccentric direction of the central shaft of the second cylinder body 42 under, when freezing cycle device 101 stopped, second piston 41 that can produce the first piston 21 of power recovery mechanism 105 and booster 102 all was positioned at the situation of top dead centre (be θ=0 °).In this case, the starting torque of power recovery mechanism 105 and booster 102 diminishes starting difficulty.

On the other hand, first piston 21 with respect to the first cylinder body 22 eccentric direction and second piston 41 of central shaft with respect in the different situation of the eccentric direction of the central shaft of the second cylinder body 42, phase place is different, is zero situation simultaneously so there are not both starting torques.Therefore, when the starting of freezing cycle device 101, start easily power recovery mechanism 105 and booster 102.

First piston 21 with respect to the first cylinder body 22 the eccentric direction of central shaft and the second piston 41 to differ 180 ° with respect to the eccentric direction of the central shaft of the second cylinder body 42 be particularly preferred.When this situation, a side starting torque were zero, the opposing party's starting torque was maximum.Therefore, the starting of power recovery mechanism 105 and booster 102 is easy especially.

(other variation)

From the viewpoint of the densification of fluid machinery 110, also can make inlet passage footpath 27, ejection path 30, suck path 47 and ejection path 50 all is formed on the first inaccessible parts 115.

On refrigerant loop 9, also can fill the cold-producing medium that the high-pressure side does not form supercriticality.Particularly, on refrigerant loop 109, for example fill Fu Liang class cold-producing medium.

Also can on the basis of

counterweight

152a and 152b, more one or more counterweights be installed on the axle 12 in addition.

Be illustrated by the example that compressor 103, gas cooler 104, power recovery mechanism 105, evaporimeter 106, booster 102 consist of about refrigerant loop 9, but refrigerant loop 9 also can also have said structure key element structural element (for example gas-liquid separator or oil eliminator) in addition.

In the above-described embodiment, are connected the example that is directly connected by axle 12 with booster about power recovery mechanism 105 and are illustrated, but the invention is not restricted to this.For example, also can connect generator in power recovery mechanism 105, and connect motor at booster 102, by the electric power that is obtained by this generator the motor that drives booster 102 be driven.

Utilizability on the industry

The present invention is useful for freezing cycle devices such as hot-warer supplying machine, refrigeration-heating air-conditioners.

Claims

1. freezing cycle device, the refrigerant loop that it has refrigerant circulation is characterized in that:

Described refrigerant loop has:

Compressor, its compressed refrigerant;

Radiator, it makes the refrigerant loses heat by described compressor compresses;

Power recovery mechanism, it sucks the ejection stroke from the cold-producing medium after the suction stroke of the cold-producing medium of described radiator and this suction of ejection basically continuously;

Evaporimeter, it makes the cold-producing medium evaporation by the ejection of described power recovery mechanism,

Described cold-producing medium is carbon dioxide,

Described power recovery mechanism possesses:

The first cylinder body, its two ends are inaccessible by the first inaccessible parts and the second inaccessible parts, and this first cylinder body has inner peripheral surface;

Rotation axle freely, its direction of principal axis at described the first cylinder body connects described the first cylinder body;

The first piston of tubular, it is supported on described axle with the state axle with respect to the eccentricity of central axis of described the first cylinder body in described the first cylinder body, and divides between the inner peripheral surface of this first piston and described the first cylinder body and form the first operating chamber;

The first partition member, it is separated into high-pressure side and low-pressure side with described the first operating chamber;

First sucks the path, and it is followed the rotation of described first piston and opens and closes, and is communicated with described on high-tension side the first operating chamber; And

The first ejection path, it is followed the rotation of described first piston and opens and closes, and is communicated with the first operating chamber of described low-pressure side,

Described first sucks the path is formed at the described first inaccessible parts or the described second inaccessible parts, and described the first ejection path is formed at the described first inaccessible parts or the described second inaccessible parts,

Described first suck path and described the first ejection path only moment that described first piston is positioned at top dead centre by described first piston locking,

Described first sucks the path at the part opening adjacent with described the first partition member of described on high-tension side the first operating chamber, and described first sucks the path forms the described first piston when being positioned at top dead centre with respect to the end limit in the outside of the opening of described the first operating chamber outer peripheral face circular-arc

Described the first ejection path is at the part opening adjacent with described the first partition member of the first operating chamber of described low-pressure side, and described the first ejection path forms outer peripheral face circular-arc of the described first piston when being positioned at top dead centre with respect to the end limit in the outside of the opening of described the first operating chamber.

2. freezing cycle device as claimed in claim 1 is characterized in that:

It is large with respect to the aperture area of described the first operating chamber that described the first ejection path sucks the path with respect to the open area ratio of described the first operating chamber described first.

3. freezing cycle device as claimed in claim 1 is characterized in that:

The bore that the relative aperture described first in described the first ejection path sucks the path is large.

4. freezing cycle device as claimed in claim 1 is characterized in that:

Consist of gaseous state from least a portion of the cold-producing medium of described power recovery mechanism ejection.

5. freezing cycle device as claimed in claim 1 is characterized in that:

Described first sucks the path at the part opening adjacent with described the first partition member of described on high-tension side the first operating chamber, and described first suck the path with respect to the peristome of described the first operating chamber to be formed obliquely at the direction of principal axis of the upwardly extending mode in the side of widening of described on high-tension side the first operating chamber with respect to described the first cylinder body.

6. freezing cycle device as claimed in claim 1 is characterized in that:

Described the first ejection path is at the part opening adjacent with described the first partition member of the first operating chamber of described low-pressure side, and described the first ejection path with respect to the peristome of described the first operating chamber to be formed obliquely at the upwardly extending mode in the side of widening of the first operating chamber of the described low-pressure side direction of principal axis with respect to the first cylinder body.

7. freezing cycle device as claimed in claim 1 is characterized in that:

The described first either party who sucks in path and described the first ejection path is formed on the described first inaccessible parts, and the opposing party is formed on the described second inaccessible parts.

8. freezing cycle device as claimed in claim 1 is characterized in that:

Described power recovery mechanism also has:

One or more other cylinder bodies, its two ends are blocked and have inner peripheral surface, and described axle connects its central shaft and locates;

Other pistons of tubular, it rotates freely with the state with respect to the eccentricity of central axis of described other cylinder bodies that the earth's axis is supported on described axle in described other cylinder bodies, and divides between the inner peripheral surface of these other pistons and described other cylinder bodies and form other operating chamber;

Other partition members, it is separated into high-pressure side and low-pressure side with described other operating chamber;

Other suck the path, and it is followed the rotation of described other pistons and opens and closes, and is communicated with described on high-tension side other operating chamber; And

Other spray the path, and it is followed the rotation of described other pistons and opens and closes, and is communicated with other operating chamber of described low-pressure side.

9. freezing cycle device as claimed in claim 8 is characterized in that:

Described a plurality of cylinder configuration becomes the position of each top dead centre equally spaced to locate on the direction of rotation of described axle.

10. freezing cycle device as claimed in claim 1 is characterized in that:

Described compressor is to have compressor shaft and be rotated the rotary type of action or the compressor of vortex centered by described compressor shaft, and described compressor shaft is connected with the described axle of described power recovery mechanism.

11. freezing cycle device as claimed in claim 1 is characterized in that:

Described the first suction path is positioned at the position than the more close described compressor in described the first ejection path.

12. freezing cycle device as claimed in claim 1 is characterized in that:

Also be provided with described axle and be connected, and the generator of the rotary electrification by described axle.

13. freezing cycle device as claimed in claim 1 is characterized in that:

Described radiator is made of the first heat exchanger and described evaporimeter is made of the second heat exchanger, and perhaps, described radiator is made of described the second heat exchanger and described evaporimeter is made of described the first heat exchanger,

Described the first heat exchanger and described the second heat exchanger arrangement and are connected with described power recovery mechanism respectively in described refrigerant loop,

Described freezing cycle device also possesses switching mechanism, it can switch the first connection status and the second connection status, described the first connection status is that the ejiction opening with described compressor is connected with described the first heat exchanger, and the suction inlet of described compressor is connected with described the second heat exchanger; Described the second connection status is that the ejiction opening with described compressor is connected with described the second heat exchanger, and the suction inlet of described compressor is connected with described the first heat exchanger, and

In described the first connection status, described the first heat exchanger plays the effect as described radiator, described the second heat exchanger plays the effect as described evaporimeter, in described the second connection status, described the first heat exchanger plays the effect as described evaporimeter, and described the second heat exchanger plays the effect as radiator.

14. freezing cycle device as claimed in claim 1 is characterized in that:

Described refrigerant loop also has booster, this booster is by the power drive of reclaiming by described power recovery mechanism, and basically sucks continuously the stroke that sprays to described compressor side from the stroke of the cold-producing medium of described evaporimeter and the cold-producing medium that will suck.

15. freezing cycle device as claimed in claim 14 is characterized in that:

Also has the closed container of taking in described power recovery mechanism and described booster.

16. freezing cycle device as claimed in claim 15 is characterized in that:

Described closed container is frozen machine oil and fills up.

17. freezing cycle device as claimed in claim 15 is characterized in that:

Described compressor has: compressor main body, its compression and ejection cold-producing medium;

Housing, it is formed with the inner space, and described compressor main body is taken in this inner space, and the cold-producing medium after compressed from described compressor main body ejection,

Be formed with the oily reservoir of accumulating the refrigerator oil that described compressor main body is lubricated in the bottom of described inner space,

Described compressor also is provided with the oil pipe of the internal communication that makes described oily reservoir and described closed container.

18. freezing cycle device as claimed in claim 17 is characterized in that:

Also possesses the throttle mechanism that is installed on the described oil pipe.

19. freezing cycle device as claimed in claim 17 is characterized in that:

The on high-tension side pressure of the described refrigerant loop of pressure ratio of the inside of described closed container is low, and higher than the pressure of the low-pressure side of described refrigerant loop.

20. freezing cycle device as claimed in claim 15 is characterized in that:

Possess:

The 3rd inaccessible parts, it is relative with the described first inaccessible parts;

The second cylinder body, its two ends are inaccessible by the described first inaccessible parts and the described the 3rd inaccessible parts, and have the central shaft shared with the central shaft of described the first cylinder body, and have inner peripheral surface;

The second piston of tubular, it is in described the second cylinder body, be bearing on the described axle with the state axle with respect to the eccentricity of central axis of described the second cylinder body, and between the inner peripheral surface of this second piston and described the second cylinder body, divide and form basically constant the second operating chamber of volume;

The second partition member, it is separated into high-pressure side and low-pressure side with described the second operating chamber;

Second sucks the path, and it is followed the rotation of described the second piston and opens and closes, and partly is communicated with the low-pressure side of described the second operating chamber; And

The second ejection path, it is followed the rotation of described the second piston and opens and closes, and is communicated with the high-pressure side part of described the second operating chamber,

Described power recovery mechanism by the described first inaccessible parts, the described second inaccessible parts, described the first cylinder body, described first piston, described the first partition member, described first suck the path, described the first ejection path consists of,

Described booster is made of the described first inaccessible parts, the described the 3rd inaccessible parts, described the second cylinder body, described the second piston, described the second partition member, described the second suction path, described the second ejection path,

21. freezing cycle device as claimed in claim 20 is characterized in that:

Described the first suction path and described the first ejection path all are formed at the described second inaccessible parts.

22. freezing cycle device as claimed in claim 20 is characterized in that:

At least one party only is positioned at the moment of top dead centre by described first piston locking at described first piston in described the first suction path and described the first ejection path.

23. freezing cycle device as claimed in claim 20 is characterized in that:

Described the second suction path and described the second ejection path all are formed at the described the 3rd inaccessible parts.

24. freezing cycle device as claimed in claim 20 is characterized in that:

At least one party only is positioned at the moment of top dead centre by described the second piston locking at described the second piston in described the second suction path and described the second ejection path.

25. freezing cycle device as claimed in claim 20 is characterized in that:

Described first piston is positioned at moment of top dead centre and described the second piston, and to be positioned at the moment of ending roughly the same.

26. freezing cycle device as claimed in claim 20 is characterized in that:

Described first piston is roughly the same with respect to the eccentric direction of the central shaft of described the second cylinder body with respect to eccentric direction and described second piston of the central shaft of described the first cylinder body.

27. freezing cycle device as claimed in claim 20 is characterized in that:

Described freezing cycle device also is provided with counterweight, and this counterweight is configured in each end of described axle, and the weight around the rotating shaft of described axle that reduces the rotary body comprise described axle and described first piston and described the second piston is uneven.

28. freezing cycle device as claimed in claim 27 is characterized in that:

The shape of described each counterweight with respect to the rotating shaft of described axle axisymmetricly.

29. freezing cycle device as claimed in claim 20 is characterized in that:

Described compressor has:

Compressor main body, its compression and ejection cold-producing medium;

Described inner space and described closed container are communicated with,

Be formed with the groove that can be slidably inserted into described the second partition member at described the second cylinder body,

The pressure of being divided by described groove and described the second partition member in the described closed container of pressure ratio in the backside space that forms is low.

30. freezing cycle device as claimed in claim 20 is characterized in that:

Divided the pressure height in described the second operating chamber of pressure ratio in the backside space that forms by described groove and described the second partition member.

31. freezing cycle device as claimed in claim 20 is characterized in that:

Dividing the backside space that forms by described groove and described the second partition member is confined space.

32. freezing cycle device as claimed in claim 20 is characterized in that:

Also possess communicating pipe, the backside space that is formed by described groove and the division of described the second partition member is communicated with described the second suction path or described the second ejection path.

33. freezing cycle device as claimed in claim 32 is characterized in that:

Make the backside space and described second that is formed by described groove and the division of described the second partition member suck the path described communicating pipe and be communicated with,

When described the second partition member slides on the direction of the volume that dwindles described backside space, the described intercommunicating pore of described the second partition member locking.